U.S. patent number 7,070,287 [Application Number 10/420,433] was granted by the patent office on 2006-07-04 for vehicular mirror system with at least one of power-fold and power-extend functionality.
This patent grant is currently assigned to Magna Donnelly Mirrors North America L.L.C.. Invention is credited to Kris D. Brown, Keith D. Foote, Kenneth C. Peterson, James A. Ruse.
United States Patent |
7,070,287 |
Foote , et al. |
July 4, 2006 |
Vehicular mirror system with at least one of power-fold and
power-extend functionality
Abstract
A motorized pivoting and extending mechanism for a vehicular
mirror assembly includes, alternatively, a force-reduction
mechanism for reducing the friction within the mechanism, and a
slip clutch mechanism for reducing overloading of the motor when
the limits of mirror extension and retraction have been reached.
Mirror power functions receive electrical power and control signals
through a circular array of electrical contacts incorporated into
the pivot connection irrespective of the pivotal orientation of the
mirror. A motor shut-off circuit is able to shut off the motor
within a predetermined period of time. The mirror can be angularly
adjusted upon movement of the mirror between the retracted and the
extended positions to maintain a common field of view for a driver
of the vehicle to prevent the extension and/or retraction of the
mirror from undesirably repositioning the field of view captured by
the mirror.
Inventors: |
Foote; Keith D. (Kentwood,
MI), Brown; Kris D. (Lake Odessa, MI), Peterson; Kenneth
C. (Comstock Park, MI), Ruse; James A. (Allegan,
MI) |
Assignee: |
Magna Donnelly Mirrors North
America L.L.C. (Kentwood, MI)
|
Family
ID: |
29588030 |
Appl.
No.: |
10/420,433 |
Filed: |
April 22, 2003 |
Prior Publication Data
|
|
|
|
Document
Identifier |
Publication Date |
|
US 20030218812 A1 |
Nov 27, 2003 |
|
Related U.S. Patent Documents
|
|
|
|
|
|
|
Application
Number |
Filing Date |
Patent Number |
Issue Date |
|
|
60319198 |
Apr 23, 2002 |
|
|
|
|
60319243 |
May 14, 2002 |
|
|
|
|
60319244 |
May 14, 2002 |
|
|
|
|
60319324 |
Jun 18, 2002 |
|
|
|
|
60319394 |
Jul 12, 2002 |
|
|
|
|
60319412 |
Jul 19, 2002 |
|
|
|
|
60319508 |
Aug 29, 2002 |
|
|
|
|
60319637 |
Oct 21, 2002 |
|
|
|
|
60319821 |
Dec 30, 2002 |
|
|
|
|
Current U.S.
Class: |
359/841 |
Current CPC
Class: |
B60R
1/074 (20130101); B60R 1/078 (20130101) |
Current International
Class: |
G02B
5/08 (20060101) |
Field of
Search: |
;359/841,873,874,877
;248/476,479 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Robinson; Mark A.
Assistant Examiner: Amari; Alessandro
Attorney, Agent or Firm: McGarry Bair PC
Parent Case Text
CROSS-REFERENCE TO RELATED APPLICATION
This application claims the benefit of U.S. provisional
applications Ser. Nos. 60/319,198, filed Apr. 23, 2002; 60/319,243,
filed May 14, 2002; 60/319,244, filed May 14, 2002; 60/319,324,
filed Jun. 18, 2002; 60/319,394, filed Jul. 12, 2002; 60/319,412,
filed Jul. 19, 2002; 60/319,508, filed Aug. 29, 2002; 60/319,637,
filed Oct. 21, 2002; and 60/319,821, filed Dec. 30, 2002, which are
incorporated herein in their entirety.
Claims
What is claimed is:
1. An external mirror system for a vehicle comprising: a fixed
portion adapted to be mounted to the vehicle; a moveable portion
pivotally mounted to the fixed portion through a normal range of
movement between a folded position and an unfolded, retracted
position defined by a pair of terminal ends, the moveable portion
having a reflective element mounted therein defining a
rearwardly-directed field of view for a driver of the vehicle; an
actuator including a motor having at least one output shaft adapted
for bi-directional rotational movement, wherein driven rotation of
the output shaft of the motor causes the movable portion to be
pivoted with respect to the fixed portion; and at least one of: a
force-modifying device operably interconnected to the actuator for
reducing a drive force required to pivot the movable portion
relative to the fixed portion within the normal range of movement
corresponding to the folded and unfolded, refracted positions and
increasing the drive force required to pivot the movable portion
relative to the fixed portion beyond one of the terminal ends of
the normal range of movement; a transmission operably
interconnected to the actuator, the actuator operably
interconnected to the moveable portion for continuous movement in a
first stage and a second stage, wherein the transmission operably
cooperates with the actuator for movement between the first stage
and the second stage, wherein in the first stage rotational
movement of the motor pivots the movable portion between a folded
position to an unfolded, retracted position and in the second stage
translates the moveable portion between the unfolded, retracted
position and an extended position; and an adjuster operably
interconnected to the reflective element, wherein the reflective
element is positioned at a first angle of reflectance and the
adjuster positions the reflective element at a second angle of
reflectance as the reflective element is moved between the
unfolded, retracted and an extended position to adjust the field of
view of the reflective element for the driver of the vehicle.
2. The external mirror system of claim 1 wherein one of the fixed
portion and the non-rotatable portion of the actuator has one of a
detent thereon and a recess therein defining the terminal ends of
the normal range of movement corresponding to the folded and
unfolded positions, and one of the moveable portion and the
rotatable portion of the actuator has the other of the detent and
the recess.
3. The external mirror system of claim 2 and further comprising at
least one spring biasing the detent and the recess together.
4. The external mirror system of claim 1 wherein the
force-modifying device comprises a pin interconnected to the
actuator for preventing contact between the detent and the recess
during the normal range of movement.
5. The external mirror system of claim 1 wherein at least one
output shaft of the motor has a proximal portion thereof
interconnected to a first linkage for pivoting the movable portion
between the folded position and the unfolded, retracted
position.
6. The external mirror system of claim 5 wherein the first linkage
comprises a rack gear operably connected to a spur gear, and the
spur gear is prevented from movement relative to the fixed portion
during the first stage.
7. The external mirror system of claim 1 wherein: the fixed portion
includes a first conductor located along a pivotal movement region;
the moveable portion includes a second conductor maintained in
operable interaction with the first conductor in the pivotal
movement region along the normal range of movement; and the
actuator has at least one terminal operably interconnected to the
second conductor; whereby operable interconnection between the
actuator and the first conductor is maintained during pivotal
movement of the moveable portion relative to the fixed portion
throughout at least the normal range of movement thereof.
8. The external mirror system of claim 7 wherein at least one of
the first and second conductors comprise a conductive material
deposited onto the surface of the corresponding fixed portion and
moveable portion.
9. The external mirror system of claim 1 wherein the adjuster
defines an arcuate path between the retracted and extended
positions and the adjustment of the field of view of the reflective
element between the first angle of reflectance and the second angle
of reflectance occurs as the reflective element is moved along the
arcuate path.
10. The external mirror system of claim 1 wherein the adjuster
further comprises one of a cam and a cam follower operably
interconnected to one of the reflective element and the moveable
portion, and the other of the cam and cam follower operably
interconnected to the fixed portion, wherein following movement of
the cam follower with the cam positions the reflective element
between the first angle of reflectance and the second angle of
reflectance when the movable portion is moved between the unfolded,
retracted and extended positions.
11. The external mirror system of claim 1 wherein the adjuster
comprises: a first arm mounted to the fixed portion and adapted to
extend laterally-outwardly from a vehicle having one of a cam and
cam follower thereon; and a second arm mounted to one of the
movable portion and the reflective element and received by the
first arm for lateral extendable and retractable movement
therewith, the second arm having the other of the cam and cam
follower thereon.
12. An external vehicular mirror system for a vehicle comprising: a
fixed portion adapted to be mounted to the vehicle; a moveable
portion adapted for a normal range of movement including a
reflective element mounted therein; an actuator including a motor
having at least one output shaft adapted for bi-directional
rotational movement, the actuator operably interconnected to the
moveable portion for continuous movement in a first stage and a
second stage, wherein in the first stage rotational movement of the
motor pivots the movable portion between a folded position to an
unfolded, retracted position and in the second stage translates the
moveable portion between the unfolded, retracted position and an
extended position; and a transmission for transitioning rotational
movement of the motor between the first and second stages.
13. The external mirror system of claim 12 wherein the at least one
output shaft of the motor has a proximal portion thereof
interconnected to a first linkage for pivoting the movable portion
between the folded position and the unfolded, retracted
position.
14. The external mirror system of claim 13 wherein the first
linkage comprises a rack gear operably connected to a spur gear,
and the spur gear is prevented from movement relative to the fixed
portion during the first stage.
15. The external mirror system of claim 14 wherein the spur gear is
moveable relative to the fixed portion when the fixed portion is
forced beyond the normal range of movement.
16. The external mirror system of claim 14 and further comprising
at least one spring for biasing the spur gear and the fixed portion
together.
17. The external mirror system of claim 12 wherein the at least one
output shaft of the motor has a distal portion thereof
interconnected to a first linkage for translating the movable
portion between the unfolded, refracted position and the extended
position.
18. The external mirror system of claim 17 wherein the first
linkage comprises a drive nut operably connected to a catch, and
the drive nut moves along the output shaft for translational
movement of the catch during the second stage.
19. The external mirror system of claim 17 wherein the transmission
comprises the drive nut wherein the drive nut is operably engaged
to the at least one output shaft of the motor, a first bracket
comprising a first slot, and a second bracket comprising a second
slot wherein, when the motor reaches a point between the proximal
and distal portions of the jackscrew, the drive nut oscillates from
the first slot to the second slot between the first linkage and a
second linkage to transfer movement of the moveable portion between
pivotal movement and extension movement.
20. The external mirror system of claim 12 wherein the motor is
pivotally mounted to the fixed portion.
21. The external mirror system of claim 12 and further comprising a
drive nut, a spur gear and a rack gear, wherein the spur gear is
associated with the fixed portion and the rack gear is associated
with the moveable portion, and the rack gear is operably engaged
with both the spur gear and the drive nut during the first
stage.
22. The external mirror system of claim 21 wherein the drive nut is
disengaged from the rack gear and operably engaged with the
reflective element during the second stage for extendable movement
along the jackscrew.
23. The external mirror system of claim 12 and further comprising a
shut-off circuit for controlling the operation of the motor.
24. The external mirror system of claim 23 wherein the shut-off
circuit comprises a switch for selecting one of operation of the
first stage and operation of the second stage.
25. The external mirror system of claim 23 wherein the shut-off
circuit comprises a switch for controlling the operation of the
first stage.
26. The external mirror system of claim 23 wherein the shut-off
circuit comprises a switch for controlling the operation of the
second stage.
27. The external mirror system of claim 12 wherein the transmission
comprises a clutch mounted to the at least one output shaft of the
motor and to the actuator, wherein the clutch driveably
interconnects the at least one output shaft of the motor to drive
the actuator in the first stage at a first motor speed, and wherein
the clutch driveably interconnects the at least one output shaft of
the motor to drive the actuator in the second stage at a second
motor speed.
28. The external mirror system of claim 27 wherein the clutch
comprises a drive surface and a driven surface.
29. The external mirror system of claim 28 wherein the drive
surface and the driven surface are biased together by at least one
spring.
30. The external mirror system of claim 27 wherein the motor
comprises a first output shaft connected to the actuator to drive
the actuator in the first stage for pivotal movement of the
moveable portion and a second output shaft connected to the
actuator to drive the actuator in the second stage for extension
movement of the moveable portion.
31. The external mirror system of claim 30 wherein the clutch is
disposed between the first output shaft and the actuator.
32. The external mirror system of claim 31 wherein the clutch
comprises a drive surface and a driven surface.
33. The external mirror system of claim 32 wherein the drive
surface is operably engaged with the driven surface when the first
output shaft is rotated at a first speed, and is operably
disengaged with the driven surface when the first output shaft is
rotated at a second speed which is slower than the first speed.
34. The external mirror system of claim 30 wherein the second
output shaft is operably disengaged from the actuator when the
second output shaft is operated at a first speed, and is operably
engaged with the actuator when the second output shaft is rotated
at a second speed which is slower than the first speed.
Description
BACKGROUND OF THE INVENTION
1. Field of the Invention
In one of its aspects, the invention relates to a vehicular mirror
assembly adapted to be mounted to a vehicle for movement between an
extended and a retracted position. More particularly, the invention
relates to a pivoting mechanism for performing the pivotal movement
of the vehicular mirror assembly including a mechanism for reducing
the friction within the pivoting mechanism. In another aspect, the
invention relates to an external vehicle mirror having both powered
folding and powered extension functionality accomplished by a
single motor. In another aspect, the invention relates to a
shut-off circuit for a DC motor and, more particularly, to a
shut-off circuit for a motor contained in a vehicular mirror which
performs a movable function for the mirror, such as linear
extension or pivotal movement. In another aspect, the invention
relates to an extendable vehicular mirror in which the mirror is
angularly adjusted upon movement of the mirror between the
retracted and the extended positions.
2. Description of the Related Art
External mirrors are ubiquitous for contemporary vehicles. External
mirrors have long been used to aid the driver in operating the
vehicle, especially in improving the rearward view of the driver.
Over time, more and more functionality has been incorporated into
the external mirrors. For example, it is common to pivot or fold
the external mirror against the vehicle body to prevent the jarring
of the mirror when the vehicle is not operated. The mirror-folding
function can incorporate a power assist, such as that disclosed in
U.S. Pat. Nos. 5,684,646 and 5,703,732, which are incorporated
herein by reference.
External mirrors are also extendable away from the vehicle, which
is useful when towing a trailer. Mirrors incorporating both the
powered fold and powered extension functionality are known and have
used separate motors for both the folding and extension functions.
Examples of such mirrors are disclosed in U.S. Pat. Nos. 6,276,808
and 6,213,609, assigned to the assignee of the current application,
and are incorporated by reference.
The power-assist devices for the mirror-folding function typically
include a motor which, upon a suitable activating signal from a
controller, drives a rotatable column through an output gear
assembly attached to the motor. The rotatable column is operably
attached to the mirror so that rotation of the column is translated
into pivoting of the mirror. The rotational movement of the mirror
is controlled in two ways. The mirror assembly is provided with
"stops" which define the outermost and innermost limits of travel
of the mirror housing between the extended and retracted positions,
respectively, and provide a positive limitation of the pivoting of
the mirror. Additionally, the controller actuates the motor for a
preset time interval at least equal to the time required to pivot
the mirror between the fully retracted and fully extended
positions. The motor may thus continue to operate after the mirror
has reached its limit of movement defined by the stops. The action
of continuing the operation of the motor even after the mirror
limit of movement has been reached means that the motor may be
forced to work against a virtually immovable obstacle in the form
of the stops. In such a case, the current load through the motor
will typically increase significantly above the normal operating
current, leading to overheating and, eventually, premature motor
failure. The increased current load can also lead to overloading
and premature failure of associated electrical circuitry, such as
the controller, or stripping or other mechanical failure of gears
and other mechanical components. Any of these failures will require
difficult and costly replacement of the failed parts.
A spring is typically provided around the rotatable column to
provide a frictional engagement between the mirror housing and a
bracket for mounting the mirror housing to the vehicle (and about
which the pivotal movement occurs). This frictional engagement is
important to ensure that the rotational movement of the mirror does
not overtravel beyond the "stops." The spring member insures that
the rotatable column is held against the mirror bracket so that,
when the extended and retracted positions are approached, a
positive engagement occurs with the stops.
While the frictional engagement is important at the outermost and
innermost limits of travel of the mirror housing with respect to
the vehicle, the friction encountered by the rotatable column
during the normal range of movement (i.e., between the extended and
retracted positions) requires that the motor draw extra current to
overcome this friction to move the mirror between the extended and
retracted positions.
The trade-off on these types of prior art vehicular mirror pivoting
devices is simple. Increasing the friction between the rotatable
column and the mirror bracket, while providing a more desirable
holding force, requires a more heavy-duty motor to drive the
rotatable column, thus increasing cost. Decreasing the friction
between the rotatable column and the mirror bracket permits the use
of a lower-torque, and thus lower cost, motor but substantially
reduces the holding force of the rotatable column against the
mirror bracket at the rotatable column pivot to the innermost
and/or the outermost retracted and extended positions,
respectively.
The mirror may incorporate other power functions such as a
motorized tilt mechanism for the reflective element, puddle lights,
or turn signal lights. Each of these functions requires electrical
connections to the vehicle power supply and onboard controls. Such
electrical connections are typically made through a wiring harness
which must necessarily pass through the mirror pivot mechanism. The
wiring harness must be constructed and routed in order to
accommodate the pivoting movement of the mirror. Thus, the wiring
harness must have both flexibility to accommodate the pivoting
movement and sufficient durability to withstand the repeated
pivoting of the mirror assembly. Nevertheless, the repeated flexing
of the wiring harness can lead to breakage of individual wires and
failure of one or more of the power functions, necessitating costly
replacements. Furthermore, the greater the number of power
functions, the larger and heavier the wiring harness required,
which can add significant weight to the mirror assembly. Finally,
fabrication and routing of the wire harness through the mirror
assembly can be complicated, requiring additional steps in the
manufacture of the mirror assembly, with consequent additional
cost.
The use of separate motors for each function is not desirable
because it increases costs and part count, which are undesirable
characteristics in the automotive parts supply industry. The extra
motor also increases the volume of the mirror housing, which is
also typically undesirable since increased volume can lead to
increased drag, which negatively impacts fuel mileage, and
increased wind-induced noise.
Every mirror to be assembled for use on a vehicle does not need to
perform the above-listed functions. For example, one mirror may
have only a powered folding function. Another mirror may have only
a powered extend function. Yet another may have neither. The costs
and labor of maintaining multiple designs and assembling different
features into a vehicle mirror are often burdensome. There is a
need to reduce cost and time in the assembly of vehicle mirrors
with multiple functionalities.
When the motor is actuated, typically a rush of current is supplied
to the motor as directed by a motor controller due to the momentum
required by the motor to move the power-assist devices. At the end
of a full range of travel of a power-assist device, the motor is
often forced to stop (typically due to a mechanical stop
encountered by the power-assist device) but power is still supplied
to the motor. If the power is not cut off, the motor can overheat
and become damaged. It is also desirable to be able to control a
motor that is operable in more than one direction since motors of
this type must typically be able to move components in both
directions (e.g., between retracted and extended positions).
Current attempts to solve this problem have typically fallen short
of a desirable solution. For example, U.S. Pat. No. 6,078,160,
issued Jun. 20, 2000, discloses a bi-directional motor control
circuit. However, it has been found that this motor control circuit
is temperature-sensitive, causing undesirable results when the
circuit is used through a wide range of ambient temperatures. It
has also been found that a resetable fuse can be provided in series
with the motor, however, this arrangement can provide an
undesirable recovery time (i.e., waiting for the fuse to
reset).
FIGS. 112 and 113 illustrate a vehicle 1310 having a prior art
extendable mirror 1312 comprising a base 1314 mounted to the
vehicle 1310 with an arm 1316 movable between a retracted position
(see FIG. 112) and an extended position (see FIG. 113). A schematic
of a driver 1318 is shown in each of FIGS. 112 113 in which the
driver's field of view is illustrated by first view field 1320
emanating from the driver 1318 to a mirror 1322 mounted to the arm
which, in turn, is reflected and extends therefrom as a second
field of view 1324. As can be seen in the extended position shown
in FIG. 113, the second field of view 1324 is positioned outwardly
of that shown in FIG. 112 due to the extension of the mirror
1322.
This can create a potential "blind spot" as shown by the shaded
region in FIG. 113 which could cause the driver 1318 to not be able
to see adjacent vehicles, creating a dangerous driving condition.
On a more practical level, it can also be annoying for the driver
to re-position the mirror manually by either manual manipulation of
the mirror 1322 or by using on-board controls (not shown) for
repositioning the mirror as is conventionally known in the art.
SUMMARY OF THE INVENTION
In one aspect, the invention relates to an external mirror system
for a vehicle comprising: a fixed portion adapted to be mounted to
the vehicle; a moveable portion pivotally mounted to the fixed
portion through a normal range of movement between a folded
position and an unfolded, retracted position defined by a pair of
terminal ends, the moveable portion having a reflective element
mounted therein defining a rearwardly-directed field of view for a
driver of the vehicle; an actuator including a motor having at
least one output shaft adapted for bi-directional rotational
movement, wherein driven rotation of the output shaft of the motor
causes the movable portion to be pivoted with respect to the fixed
portion; and at least one of: a force-modifying device operably
interconnected to the actuator for reducing a drive force required
to pivot the movable portion relative to the fixed portion within
the normal range of movement corresponding to the folded and
unfolded, retracted positions and increasing the drive force
required to pivot the movable portion relative to the fixed portion
beyond one of the terminal ends of the normal range of movement; a
transmission operably interconnected to the actuator, the actuator
operably interconnected to the moveable portion for continuous
movement in a first stage and a second stage, wherein the
transmission operably cooperates with the actuator for movement
between the first stage and the second stage, wherein in the first
stage rotational movement of the motor pivots the movable portion
between a folded position to an unfolded, retracted position and in
the second stage translates the moveable portion between the
unfolded, retracted position and an extended position; and an
adjuster operably interconnected to the reflective element, wherein
the reflective element is positioned at a first angle of
reflectance and the adjuster positions the reflective element at a
second angle of reflectance as the reflective element is moved
between the unfolded, retracted and an extended position to adjust
the field of view of the reflective element for the driver of the
vehicle.
In various embodiments of the invention, one of the fixed portion
and the non-rotatable portion of the actuator can have one of a
detent thereon and a recess therein defining the terminal ends of
the normal range of movement corresponding to the folded and
unfolded positions, and one of the moveable portion and the
rotatable portion of the actuator can have the other of the detent
and the recess. At least one spring can bias the detent and the
recess together. The force-modifying device can comprise a pin
interconnected to the actuator for preventing contact between the
detent and the recess during the normal range of movement. At least
one output shaft of the motor can have a proximal portion thereof
interconnected to a first linkage for pivoting the movable portion
between the folded position and the unfolded, retracted
position.
The first linkage can comprise a rack gear operably connected to a
spur gear, and the spur gear can be prevented from movement
relative to the fixed portion during the first stage. The fixed
portion can include a first conductor located along a pivotal
movement region; the moveable portion can include a second
conductor maintained in operable interaction with the first
conductor in the pivotal movement region along the normal range of
movement; and the actuator can have at least one terminal operably
interconnected to the second conductor. Operable interconnection is
thereby maintained between the actuator and the first conductor
during pivotal movement of the moveable portion relative to the
fixed portion throughout at least the normal range of movement
thereof.
At least one of the first and second conductors can comprise a
conductive material deposited onto the surface of the corresponding
fixed portion and moveable portion. The adjuster can define an
arcuate path between the retracted and extended positions and the
adjustment of the field of view of the reflective element between
the first angle of reflectance and the second angle of reflectance
occurs as the reflective element is moved along the arcuate
path.
The adjuster can further comprise one of a cam and a cam follower
operably interconnected to one of the reflective element and the
moveable portion, and the other of the cam and cam follower
operably interconnected to the fixed portion, wherein following
movement of the cam follower with the cam can position the
reflective element between the first angle of reflectance and the
second angle of reflectance when the movable portion is moved
between the unfolded, retracted and extended positions.
The adjuster can also comprise: a first arm mounted to the fixed
portion and adapted to extend laterally-outwardly from a vehicle
having one of a cam and cam follower thereon; and a second arm
mounted to one of the movable portion and the reflective element
and received by the first arm for lateral extendable and
retractable movement therewith, the second arm having the other of
the cam and cam follower thereon.
In another aspect of the invention, an external mirror system for a
vehicle comprises: a fixed portion adapted to be mounted to the
vehicle; a moveable portion pivotally mounted to the fixed portion
through a normal range of movement between a folded position and an
unfolded position defined by a pair of terminal ends, the moveable
portion having a reflective element mounted therein; an actuator
having a non-rotatable portion mounted to the fixed portion and a
rotatable portion mounted to the movable portion, wherein relative
rotation of the rotatable portion of the actuator with respect to
the non-rotatable portion causes the movable portion to be pivoted
with respect to the fixed portion; and a force-modifying device
operably interconnected to the actuator for reducing a drive force
required to pivot the movable portion relative to the fixed portion
within the normal range of movement corresponding to the folded and
unfolded positions and increasing the drive force required to pivot
the movable portion relative to the fixed portion beyond one of the
terminal ends of the normal range of movement.
Various embodiments of the invention are also contemplated. One of
the fixed portion and the non-rotatable portion of the actuator can
have one of a detent thereon and a recess therein defining the
terminal ends of the normal range of movement corresponding to the
folded and unfolded positions, and one of the moveable portion and
the rotatable portion of the actuator can have the other of the
detent and the recess. At least one spring can bias the detent and
the recess together. The force-modifying device can comprise a pin
interconnected to the actuator for preventing contact between the
detent and the recess during the normal range of movement. The
force-modifying device can comprise a ring interconnected to the
actuator for preventing contact between the detent and the recess
during the normal range of movement. The ring can be C-shaped.
The actuator can further comprise a motive element for driving the
rotatable portion of the actuator to pivot the moveable portion
between the folded and unfolded positions. The motive element can
comprise a motor. The force-modifying device can further comprise a
clutch disposed between the motor and the rotatable portion of the
actuator. The clutch can engage the rotatable portion of the
actuator within the normal range of movement and can disengage
therefrom when the moveable portion is forced beyond one of the
terminal ends. The clutch can comprise a drive surface and a driven
surface. The drive surface and the driven surface can be biased
together by at least one spring.
In another aspect of the invention, the invention relates to an
external vehicular mirror system for a vehicle comprising: a fixed
portion adapted to be mounted to the vehicle; a moveable portion
adapted for a normal range of movement including a reflective
element mounted therein; an actuator including a motor having at
least one output shaft adapted for bi-directional rotational
movement, the actuator operably interconnected to the moveable
portion for continuous movement in a first stage and a second
stage, wherein in the first stage rotational movement of the motor
pivots the movable portion between a folded position to an
unfolded, retracted position and in the second stage translates the
moveable portion between the unfolded, retracted position and an
extended position; and a transmission for transitioning rotational
movement of the motor between the first and second stages.
Various embodiments of the invention are also contemplated. The at
least one output shaft of the motor can have a proximal portion
thereof interconnected to a first linkage for pivoting the movable
portion between the folded position and the unfolded, retracted
position. The first linkage can comprise a rack gear operably
connected to a spur gear, and the spur gear is prevented from
movement relative to the fixed portion during the first stage. The
spur gear can be moveable relative to the fixed portion when the
fixed portion is forced beyond the normal range of movement. The
external mirror can further comprise at least one spring for
biasing the spur gear and the fixed portion together.
The at least one output shaft of the motor can have a distal
portion thereof interconnected to a second linkage for translating
the movable portion between the unfolded, retracted position and
the extended position. The second linkage can comprise a drive nut
operably connected to a catch, and the drive nut can move along the
output shaft for translational movement of the catch during the
second stage. The transmission can comprise the drive nut wherein
the drive nut is operably engaged to the at least one output shaft
of the motor, a first bracket comprising a first slot, and a second
bracket comprising a second slot wherein, when the motor reaches a
point between the proximal and distal portions of the jackscrew,
the drive nut oscillates from the first slot to the second slot
between the first linkage and the second linkage to transfer
movement of the moveable portion between pivotal movement and
extension movement.
The motor can be pivotally mounted to the fixed portion. The spur
gear can be associated with the fixed portion and the rack gear can
be associated with the moveable portion, and the rack gear can be
operably engaged with both the spur gear and the drive nut during
the first stage. The drive nut can be disengaged from the rack gear
and operably engaged with the reflective element during the second
stage for extendable movement along the jackscrew.
A shut-off circuit can be provided for controlling the operation of
the motor. The shut-off circuit can comprise a first switch for
selecting one of operation of the first stage and operation of the
second stage. The shut-off circuit can comprise a second switch for
controlling the operation of the first stage. The shut-off circuit
can comprise a third switch for controlling the operation of the
second stage. The transmission can comprise a clutch mounted to the
at least one output shaft of the motor and to the actuator, wherein
the clutch can driveably interconnect the at least one output shaft
of the motor to drive the actuator in the first stage at a first
motor speed, and wherein the clutch can driveably interconnect the
at least one output shaft of the motor to drive the actuator in the
second stage at a second motor speed.
The clutch can comprise a drive surface and a driven surface. The
drive surface and the driven surface can be biased together by at
least one spring. The motor can comprise a first output shaft
connected to the actuator to drive the actuator in the first stage
for pivotal movement of the moveable portion and a second output
shaft connected to the actuator to drive the actuator in the second
stage for extension movement of the moveable portion. The clutch
can be disposed between the first output shaft and the actuator.
The drive surface can be operably engaged with the driven surface
when the first output shaft is rotated at a first speed, and can be
operably disengaged with the driven surface when the first output
shaft is rotated at a second speed which is slower than the first
speed. The second output shaft can be operably disengaged from the
actuator when the second output shaft is operated at a first speed,
and can be operably engaged with the actuator when the second
output shaft is rotated at a second speed which is slower than the
first speed.
In an addition aspect, the invention relates to an external mirror
system for a vehicle comprising: a fixed portion adapted to be
mounted to the vehicle; a moveable portion including a reflective
element mounted therein; and a functionality module mounted at one
part to the fixed portion and at another part to the moveable
portion, the functionality module including a plurality of mounts
for operably mounting one of the movement functionality components
in universal interconnection fashion selected from the group
consisting of: a powered-fold, powered-extend mechanism; a
powered-fold, manual-extend mechanism; a manual-fold,
powered-extend mechanism; a manual-fold, manual-extend mechanism; a
powered-fold mechanism; a powered-extend mechanism; a manual-extend
mechanism; and a manual-fold mechanism. The functionality module is
thereby capable of operably mounting a plurality of the movement
functionality components.
The movement functionality component corresponding to the
manual-fold, powered-extend mechanism can comprises at least one
motive element, a first linkage interconnected to the at least one
motive element for pivoting the moveable portion between a folded
position and a retracted, unfolded position, and a second linkage
interconnected to the at least one motive element for translating
the moveable portion between the retracted, unfolded position and
an extended, unfolded position.
The movement functionality component corresponding to the
powered-fold, manual-extend mechanism can comprise at least one
motive element, a first linkage interconnected to the at least one
motive element for pivoting the moveable portion between a folded
position and a retracted, unfolded position, and a second linkage
responsive to an externally-applied manual force for translating
the moveable portion between a retracted, unfolded position and an
extended position.
The movement functionality component corresponding to the
manual-fold, powered-extend mechanism can comprise at least one
motive element, a first linkage responsive to an externally-applied
manual force for pivoting the moveable portion between a folded
position and a retracted, unfolded position, and a second linkage
interconnected to the at least one motive element for translating
the moveable portion between a retracted, unfolded position and an
extended position.
The movement functionality component corresponding to the
manual-fold, manual-extend mechanism can comprise a first linkage
responsive to an externally-applied manual force for pivoting the
moveable portion between a folded position and a retracted,
unfolded position, and a second linkage responsive to an
externally-applied manual force for translating the moveable
portion between a retracted, unfolded position and an extended
position.
The movement functionality component corresponding to the
powered-fold mechanism can comprise at least one motive element,
and a linkage interconnected to the at least one motive element for
pivoting the moveable portion between a folded position and a
unfolded position.
The movement functionality component corresponding to the
powered-extend mechanism can comprise at least one motive element,
and a linkage interconnected to the at least one motive element for
translating the moveable portion between a retracted position and
an extended position.
The movement functionality component corresponding to the
manual-extend mechanism can comprise a linkage responsive to an
externally-applied manual force for translating the moveable
portion between a retracted position and an extended position.
The movement functionality component corresponding to the
manual-fold mechanism can comprise a linkage responsive to an
externally-applied manual force for pivoting the moveable portion
between a folded position and an unfolded position.
In an additional aspect, the invention relates to a method for
assembling an external mirror system for a vehicle comprising the
steps of: providing a fixed portion adapted to be mounted to the
vehicle; providing a moveable portion; providing a plurality of
movement functionality components selected from the group
consisting of: a powered-fold, powered-extend mechanism, a
powered-fold, manual-extend mechanism, a manual-fold,
powered-extend mechanism, a manual-fold, manual-extend mechanism, a
powered-fold mechanism, a powered-extend mechanism, a manual-extend
mechanism, and a manual-fold mechanism; providing a universal
mounting module adapted to receive one of each of the group of
movement functionality components; selecting one of the movement
functionality components from the group; mounting the selected
movement functionality component to the universal mounting module;
and mounting the universal mounting module at one part to the fixed
portion and at another part to the moveable portion.
Various embodiments of the invention are also contemplated. The
method can also comprise the step of mounting a reflective element
within the moveable portion. The method can also comprise the step
of removing the universal mounting module from the external mirror
system and removing the selected movement functionality component
therefrom. The method can also comprise the step of selecting
another of the movement functionality components from the group.
The method can also comprise the step of mounting the
newly-selected movement functionality component to the universal
mounting module. The method can also comprise the step of
remounting the universal mounting module at one part to the fixed
portion and at another part to the moveable portion.
In yet another aspect, the invention relates to an external mirror
system for a vehicle comprising: a fixed portion adapted to be
mounted to the vehicle including a first conductor located along a
pivotal movement region; a moveable portion pivotally mounted to
the fixed portion through a normal range of movement between folded
position and an unfolded position, the moveable portion including a
second conductor maintained in operable interaction with the first
conductor in the pivotal movement region along the normal range of
movement, the moveable portion including a reflective element
mounted therein; and an actuator operably interconnected to the
reflective element for adjustment of the position of the reflective
element, the actuator having at least one terminal operably
interconnected to the second conductor. Operable interconnection is
thereby maintained between the actuator and the first conductor
during pivotal movement of the moveable portion relative to the
fixed portion throughout at least the normal range of movement
thereof.
The at least one of the first and second conductors can comprise a
conductive material deposited onto the surface of the corresponding
fixed portion and moveable portion. The first conductor and the
second conductor can each comprise a plurality of conductive tracks
in operable communication with the plurality of conductive tracks
on the other of the first conductor and the second conductor. The
plurality of conductive tracks can be isolated from one another.
The first and second conductors can conduct electricity. A heater
can be operably interconnected to the reflective element and can
have at least one terminal thereon. A third conductor can be
operably interconnected at one portion to at least one of the
actuator and the second conductor and at another portion to the at
least one terminal of the heater. The movable portion can have a
first pivot portion and the reflective element can have a back side
with a second pivot portion, the first and second pivot portions
can be received by one another to form a universal pivot between
the movable portion and the reflective element.
A third conductor can be operably interconnected at one portion to
at least one of the actuator and the second conductor and can
terminate at another portion at the first pivot portion. A fourth
conductor can be operably interconnected at one portion to a mirror
system component and can terminate at another portion at the second
pivot portion. The third and fourth conductors can be operably
interconnected to one another through the universal pivot. The
mirror system component can be at least one of a heater, an
illumination device, a reflective element dimming device, an
actuator for performing a mirror function, a mirror positioning
device, a mirror position feedback device, a blind zone indicator
and a mirror function sensor.
In another aspect, the invention relates to an external mirror
system for a vehicle comprising: a first portion having a first
mounting portion adapted to be mounted to the vehicle, a second
mounting portion, and a first conductor extending between the first
mounting portion and the second mounting portion, wherein the first
conductor has a first terminal end in register with the vehicle
mounting portion and a second terminal end in register with the
second mounting portion; a second portion with a mounting portion
thereon and having a reflective element mounted therein, the second
portion having a second conductor extending from the mounting
portion, wherein the second conductor has a first terminal end in
register with the mounting portion and a second terminal end;
wherein, when the mounting portion of the second portion is mounted
to the second mounting portion of the first portion, the first
terminal end of the second conductor is brought into operable
communication with the second terminal end of the first conductor
thus operably interconnecting the second terminal end of the second
conductor with the first terminal end of the first conductor simply
by virtue of the mounting between the first and second portions of
the external mirror system.
At least one of the first and second conductors can comprise a
conductive material deposited onto the surface of the corresponding
first and second portions. The first conductor and the second
conductor can each comprise a plurality of conductive tracks in
operable communication with the plurality of conductive tracks on
the other of the first conductor and the second conductor. The
plurality of conductive tracks can be isolated from one another.
The first and second conductors conduct electricity. The second
terminal end of the second conductor can be interconnected to a
functional mirror component to supply power thereto. The mirror
component can comprise at least one of a heater, an illumination
device, a reflective element dimming device, an actuator for
performing a mirror function, a mirror positioning device, a mirror
position feedback device, a blind zone indicator and a mirror
function sensor.
In yet an additional aspect, the invention relates to an external
mirror system for a vehicle comprising: a fixed portion adapted to
be mounted to the vehicle; a moveable portion movably mounted to
the fixed portion between a retracted position and a
laterally-extended position relative to the fixed portion; a
reflective element movably mounted to the moveable portion at a
first angle of reflectance with respect to a driver of the vehicle
for providing a rearwardly-directed field of view; an adjuster
operably interconnected to the reflective element to position the
reflective element at a second angle of reflectance as the
reflective element is moved between the retracted and extended
positions to adjust the field of view of the reflective element for
the driver of the vehicle.
Various embodiments of the invention are also contemplated. The
adjuster can define an arcuate path between the retracted and
extended positions and the adjustment of the field of view of the
reflective element between the first angle of reflectance and the
second angle of reflectance occurs as the reflective element is
moved along the arcuate path. The adjuster can comprise a first
arcuate arm mounted to the fixed portion and adapted to extend
laterally-outwardly from a vehicle; and a second arcuate arm
mounted to the movable portion and received by the first arcuate
arm for lateral extendable and retractable movement therewith. The
reflective element can be mounted to the second arcuate arm.
A motive element, actuatable from a signal, can be provided for
moving the second arm between the retracted and extended positions.
The motive element can further comprise a motor with a threaded
output shaft, and a nut threadingly received on the output shaft
and operably interconnected to the reflective element for moving
the reflective element between the extended and retracted
positions. The adjuster can comprise a first arcuate arm mounted to
the fixed portion and adapted to extend laterall-outwardly from a
vehicle; and a second arcuate arm mounted to the movable portion
and received by the first arcuate arm for lateral extendable and
retractable movement therewith.
The adjuster can comprise one of a cam and cam follower operably
interconnected to the reflective element, and the other of the cam
and cam follower operably interconnected to one of the fixed
portion and the moveable portion. The cam and cam follower can be
operably interconnected to one another to position the reflective
element between the first angle of reflectance and the second angle
of reflectance when the movable portion is moved between the
retracted and extended positions. The adjuster can comprise a first
arm mounted to the fixed portion and adapted to extend
laterally-outwardly from a vehicle having one of the cam and cam
follower thereon; and a second arm mounted to the movable portion
and received by the first arm for lateral extendable and
retractable movement therewith, the second arm having the other of
the cam and cam follower thereon.
One of a cam and a cam follower can be operably interconnected to
one of the reflective element and the moveable portion, and the
other of the cam and cam follower can be operably interconnected to
the fixed portion, wherein following movement of the cam follower
with the cam can position the reflective element between the first
angle of reflectance and the second angle of reflectance when the
movable portion is moved between the retracted and extended
positions. The adjuster can comprise a first arm mounted to the
fixed portion and adapted to extend laterally-outwardly from a
vehicle having one of a cam and cam follower thereon; and a second
arm mounted to one of the movable portion and the reflective
element and received by the first arm for lateral extendable and
retractable movement therewith, the second arm having the other of
the cam and cam follower thereon.
BRIEF DESCRIPTION OF THE DRAWINGS
In the drawings:
FIG. 1 is a front, elevational view of a first embodiment of a
vehicular mirror assembly located in an extended, use position
comprising a mirror housing pivotally connected to a base which, in
turn, is adapted to be mounted to a vehicle, the mirror assembly
being pivotally connected to the base by a first embodiment of a
pivot mechanism including a pivoting force reduction mechanism
according to the invention.
FIG. 2 is a top plan view of the vehicular mirror assembly of FIG.
1 in the extended, use position.
FIG. 3 is a front, elevational view of the vehicular mirror
assembly of FIG. 1 showing the mirror housing pivoted relative to
the base to a retracted, stored position.
FIG. 4 is a top plan view of the vehicular mirror assembly of FIG.
1 in the retracted, stored position.
FIG. 5 is an exploded, perspective view of the vehicular mirror
assembly of FIG. 1 showing an upper portion of the base, the pivot
mechanism including the pivoting force reduction mechanism
according to the invention, and a lower portion of the base.
FIG. 6 is a perspective view of the upper portion of the base of
FIG. 5 detailing an underside portion thereof.
FIG. 7 is an exploded, perspective view of the components of FIG.
5, specifically exploding the pivot mechanism shown therein.
FIG. 8 is a perspective view of the pivot mechanism including the
pivoting force reduction mechanism of FIG. 5.
FIG. 9 is a cross-sectional view taken along line 9--9 of FIG. 5
showing the assembled pivot mechanism having the pivoting force
reduction mechanism in an activated state.
FIG. 10 is a cross-sectional view orthogonal to the view taken
along line 9--9 of FIG. 5 showing the pivot mechanism having the
pivoting force reduction mechanism in the activated state.
FIG. 11 is a perspective view in a similar orientation as FIG. 8
showing the pivot mechanism including the pivoting force reduction
mechanism in the activated state.
FIG. 12 is a cross-sectional view taken along line 12--12 of FIG. 5
showing the pivot mechanism having the pivoting force reduction
mechanism in a deactivated state.
FIG. 13 is a cross-sectional view orthogonal to the view taken
along line 12--12 of FIG. 5 showing the pivot mechanism having the
pivoting force reduction mechanism in the deactivated state.
FIG. 14 is a perspective view in a similar orientation as FIG. 8
showing the pivot mechanism including the pivoting force reduction
mechanism in the deactivated state.
FIG. 15 into a perspective view of a second embodiment of a
vehicular mirror assembly located in an extended, use position also
comprising a mirror housing pivotally connected to a base which, in
turn, is adapted to be mounted to vehicle, the mirror housing being
pivotally connected to the base by a second embodiment of a pivot
mechanism having a pivoting force reduction mechanism therein.
FIG. 16 is a top plan view of the vehicular mirror assembly of FIG.
15 shown in the extended, use position.
FIG. 17 is a top plan view of the vehicular mirror assembly of FIG.
15 shown pivoted by the pivot mechanism to a retracted, stored
position.
FIG. 18 is an exploded, perspective view of the vehicular mirror
assembly of FIG. 15 showing a bracket on the mirror housing aligned
with the pivot mechanism and with a corresponding recess on the
base.
FIG. 19 is an exploded perspective view of the pivot mechanism
shown in FIG. 18 with the remaining components of the vehicular
mirror assembly of FIG. 15 removed for purposes of clarity.
FIG. 20 is a cross-sectional view taken along line 20--20 of FIG.
19.
FIG. 21 is an exploded view of a third embodiment of a pivot
mechanism for use with the vehicular mirror assembly of FIGS. 1 and
15.
FIG. 22 is a perspective view of an outer housing comprising a
portion of the pivot mechanism of FIG. 21.
FIG. 23 is a perspective view of the interior of the outer housing
of FIG. 22.
FIG. 24 is an exploded view of a ramp, a wave spring, and an
actuator sub comprising a portion of the pivot mechanism of FIG.
21.
FIG. 25 is a perspective view of the ramp of FIG. 24.
FIG. 26 is a perspective view of the wave spring of FIG. 24.
FIG. 27 is a perspective view of the interior of the actuator sub
of FIG. 24.
FIG. 28 is an exploded view of a spring, an actuator sub ring, and
a ring gear comprising a portion of the pivot mechanism of FIG.
21.
FIG. 29 is a perspective view of the interior of the actuator sub
of FIG. 24 showing the spring, the actuator sub ring, the ring
gear, and a C-ring installed therein.
FIG. 30 is an exploded view of a motor housing and a motor
comprising a portion of the pivot mechanism of FIG. 21.
FIG. 31 is a perspective view of the interior of the motor housing
of FIG. 30.
FIG. 32 is an exploded view of the motor, a gear assembly, and an
actuator sub base comprising a portion of the pivot mechanism of
FIG. 21.
FIG. 33 is an exploded view of a portion of the gear assembly of
FIG. 32.
FIG. 34 is a perspective view of the actuator sub base of FIG.
32.
FIG. 35 is a perspective view of the actuator sub base of FIG. 34
showing the gear assembly installed.
FIG. 36 is a first perspective view of the pivot mechanism of FIG.
21 with the actuator sub base removed showing the relative
locations of the motor, the gear assembly and the actuator sub.
FIG. 37 is a second perspective view of the pivot mechanism of FIG.
36.
FIG. 38 is a perspective view of the assembled pivot mechanism of
FIG. 21.
FIG. 39 is a first perspective view of the actuator sub base and
the gear assembly of FIG. 35 showing the rotation of the gears
during operation of the pivot mechanism for pivoting the vehicular
mirror assembly.
FIG. 40 is a second perspective view of the actuator sub base and
the gear assembly of FIG. 35 showing the operation of the slip
clutch according to the invention.
FIG. 41 is a left-front perspective view of a fourth embodiment of
a vehicular mirror assembly comprising power fold and power extend
functions according to the invention and comprising a mirror
assembly rotatably mounted to a support bracket adapted to mount to
a vehicle, with the mirror assembly shown in an unfolded and
retracted position.
FIG. 42 is an exploded view of the power fold mirror of FIG. 41 and
illustrates the major components comprising a drive assembly
connecting the mirror assembly to the support bracket and for
rotating and extending the mirror assembly relative to the vehicle,
with the drive assembly comprising a drive screw having a drive nut
guided by a guide bracket and that couples with either a rack gear
to rotate the mirror housing or a mirror bracket to extend the
mirror housing.
FIG. 43 is a upper-rear perspective view of the mirror bracket of
the mirror assembly of FIG. 42 and which is adapted to support the
mirror for rotatable movement.
FIG. 44 is an upper-front perspective view of the mirror bracket of
FIG. 43.
FIG. 45 is a lower-rear perspective view of a guide bracket for the
mirror assembly illustrated in FIG. 42.
FIG. 46 is an upper-front perspective view of the guide bracket of
FIG. 45.
FIG. 47 is a perspective view similar to FIG. 41 and illustrating a
mirror housing of the mirror assembly partially exploded from the
mirror assembly to illustrate the relationship of the drive
assembly to the mirror assembly and the support bracket.
FIG. 48 is a view perpendicular to the mirror bracket of the power
fold mirror of FIG. 53 with the mirror housing removed for
clarity.
FIG. 49 is a sectional view taken along line 49--49 of FIG. 48 and
illustrating the relative position of the drive nut and a cam
pivotally mounted to the guide bracket as the drive nut is located
on the drive screw at the position corresponding to the unfolded
position and ready to transition from contact with the rack gear to
the mirror bracket to initiate the extension of the mirror housing
upon further rotation of the drive screw.
FIG. 50 is a front perspective view of the power fold mirror of
FIG. 41 shown in a folded and retracted position.
FIG. 51 is a partial exploded view similar to FIG. 47 and
illustrating the mirror housing partially exploded from the mirror
assembly to illustrate the relationship of the drive assembly to
the mirror assembly and the support bracket when the mirror
assembly is in the folded and retracted position, with the guide
bracket partially broken away to show the connection between the
drive nut and the rack gear.
FIG. 52 is a view perpendicular to the mirror bracket of the mirror
assembly of FIG. 49 with the mirror housing removed for
clarity.
FIG. 53 is a sectional view taken along line 53--53 of FIG. 52 and
illustrating the position of the drive nut relative to the guide
bracket when the mirror is in the folded and retracted
position.
FIG. 54 is a top-right perspective view of the power fold mirror
shown in the unfolded and retracted position.
FIG. 55 is similar to FIGS. 47 and 51 except that the drive nut has
transitioned from contact with the rack gear to contact with the
mirror bracket to position the drive gear at the beginning of the
extension of the mirror assembly.
FIG. 56 is a view perpendicular to the mirror bracket of the mirror
assembly of FIG. 55 with the mirror housing removed for
clarity.
FIG. 57 is a sectional view taken along line 57--57 of FIG. 56 and
illustrating the position of the drive nut relative to the mirror
bracket at the initiation of the extension of the mirror from the
retracted to extended position.
FIG. 58 is a top-right perspective view of the power fold mirror
shown in the unfolded and extended position.
FIG. 59 is similar to FIGS. 47, 51 and 55 except that the drive nut
is located on the drive screw at a position corresponding to the
extended position of the mirror assembly.
FIG. 60 is a view perpendicular to the mirror bracket of the mirror
assembly of FIG. 59 with the mirror housing removed for
clarity.
FIG. 61 is a sectional view taken along line 61--61 of FIG. 60 and
illustrating the position of the drive nut relative to the mirror
bracket and the guide bracket at the termination of the extension
of the mirror from the retracted to extension position.
FIG. 62 is a schematic of a control circuit for controlling the
folding and extending functions of the mirror.
FIG. 63 is a schematic of another embodiment of a control circuit
for controlling the folding and extending functions of the
mirror.
FIG. 64 is an exploded view of a fifth embodiment of the vehicular
mirror assembly and illustrates the major components comprising a
second embodiment of the drive assembly of FIG. 41 connecting the
mirror assembly to the support bracket and for rotating and
extending the mirror assembly relative to the vehicle, with the
drive assembly comprising a drive screw having a drive nut guided
by a guide bracket and that couples with either a rack gear to
rotate the mirror housing or a mirror bracket to extend the mirror
housing.
FIG. 65 is a lower-rear perspective view of a guide bracket for the
mirror assembly illustrated in FIG. 64.
FIG. 66 is a perspective view of the partially assembled mirror
assembly of FIG. 64 Figure illustrating a mirror housing of the
mirror assembly partially exploded from the mirror assembly to
illustrate the relationship of the drive assembly to the mirror
assembly and the support bracket.
FIG. 67 is a view perpendicular to the mirror bracket of the
vehicular mirror assembly of FIG. 72 with the mirror housing
removed for clarity.
FIG. 68 is a sectional view taken along line 68--68 of FIG. 67 and
illustrating the relative position of the drive nut and a cam
pivotally mounted to the guide bracket as the drive nut is located
on the drive screw at the position corresponding to the unfolded
position and ready to transition from contact with the rack gear to
the mirror bracket to initiate the extension of the mirror housing
upon further rotation of the drive screw.
FIG. 69 is a front perspective view of the vehicular mirror
assembly of FIG. 64 shown in a folded and retracted position.
FIG. 70 is a partial exploded view similar to FIG. 66 and
illustrating the mirror housing partially exploded from the mirror
assembly to illustrate the relationship of the drive assembly to
the mirror assembly and the support bracket when the mirror
assembly is in the folded and retracted position, with the guide
bracket partially broken away to show the connection between the
drive nut and the rack gear.
FIG. 71 is a view perpendicular to the mirror bracket of the mirror
assembly of FIG. 68 with the mirror housing removed for
clarity.
FIG. 72 is a sectional view taken along line 72--72 of FIG. 71 and
illustrating the position of the drive nut relative to the guide
bracket when the mirror is in the folded and retracted
position.
FIG. 73 is a top-right perspective view of the vehicular mirror
assembly shown in the unfolded and retracted position.
FIG. 74 is similar to FIGS. 66 and 70 except that the drive nut has
transitioned from contact with the rack gear to contact with the
mirror bracket to position the drive gear at the beginning of the
extension of the mirror assembly.
FIG. 75 is a view perpendicular to the mirror bracket of the mirror
assembly of FIG. 74 with the mirror housing removed for
clarity.
FIG. 76 is a sectional view taken along line 76--76 of FIG. 75 and
illustrating the position of the drive nut relative to the mirror
bracket at the initiation of the extension of the mirror from the
retracted to extended position.
FIG. 77 is a top-right perspective view of the vehicular mirror
assembly shown in the unfolded and extended position.
FIG. 78 is similar to FIGS. 66, 70 and 74 except that the drive nut
is located on the drive screw at a position corresponding to the
extended position of the mirror assembly.
FIG. 79 is a view perpendicular to the mirror bracket of the mirror
assembly of FIG. 78 with the mirror housing removed for
clarity.
FIG. 80 is a sectional view taken along line 80--80 of FIG. 79 and
illustrating the position of the drive nut relative to the mirror
bracket and the guide bracket at the termination of the extension
of the mirror from the retracted to extended position.
FIG. 81 is an exploded view of a vehicular mirror assembly similar
to FIG. 64, but comprising only the components for the power-fold
function.
FIG. 82 is an exploded view of the vehicular mirror assembly
similar to FIGS. 64 and 81, but comprising only the components for
the power-extension function.
FIG. 83 is an exploded view of the mirror similar to FIGS. 64, 81,
and 82, but comprising only the components for a manual-fold
function.
FIG. 84 is an exploded view of components arranged for a basic
module according to the invention.
FIG. 85 is an exploded view of components in a module arranged for
the power-extend function.
FIG. 86 is an exploded view of components in a module arranged for
the power-fold function.
FIG. 87 is an exploded view of components in a module arranged for
both the power-extend function and the power-fold function.
FIG. 88 is a close-up perspective view of the interior of the
vehicular mirror assembly of FIG. 1 showing a sixth embodiment of a
pivot mechanism for use with the vehicular mirror assembly of FIGS.
1 and 15.
FIG. 89 is an alternate close-up perspective view of the interior
of the vehicular mirror assembly shown in FIG. 88.
FIG. 90 is a perspective view of a frame comprising a portion of
the vehicular mirror assembly of FIG. 88.
FIG. 91 is a perspective view from beneath the frame of a drive
assembly and pivot assembly comprising a portion of the vehicular
mirror assembly of FIG. 88.
FIG. 92 is a perspective view of the drive assembly of FIG. 91 with
non-essential elements removed for clarity.
FIG. 93 is an elevation view of a helical gear and a clutch gear
comprising a portion of the drive assembly of FIG. 92.
FIG. 94 is a perspective view of the clutch gear of FIG. 93.
FIG. 95 is a perspective view of a pivot frame for pivotably
mounting the frame, drive assembly, and pivot assembly of FIG. 91
thereto.
FIG. 96 is a close-up perspective view of a portion of the pivot
frame of FIG. 95.
FIG. 97 is a sectional view taken along line 97--97 of FIG. 89.
FIG. 98 is a perspective view of an element of the pivot assembly
comprising a portion of the vehicular mirror assembly of FIG.
88.
FIG. 99 is a close-up perspective view of the interior of the
vehicular mirror assembly of FIG. 1 showing a seventh embodiment of
a vehicular mirror assembly having a pivot connection connecting
the reflective element assembly to the base for use with the
vehicular mirror assembly of FIGS. 1 and 15.
FIG. 100 is a perspective view with portions in phantom of the
reflective element assembly and pivot connection of FIG. 99 showing
the electrical connection of a motorized reflective element tilt
actuator to the vehicle's power supply and on-board controls
through an electrical routing assembly integrated into the pivot
connection according to the invention.
FIG. 101 is a perspective view with portions in phantom of the
reflective element assembly shown in FIG. 100 illustrating a
portion of the electrical routing assembly.
FIG. 102 is a perspective view with portions in phantom of the base
shown in FIG. 100 illustrating a portion of the electrical routing
assembly.
FIG. 103 is a perspective view of an alternative embodiment of the
electrical routing assembly of FIGS. 99 102 showing a bracket
portion of the mirror assembly in phantom and having the mirror
housing removed both for purposes of clarity to show features of
this embodiment relating to the provision of a routing system for a
heater element through a mirror pivot portion.
FIG. 104 is an enlarged perspective view paying particular
attention to the interengagement of a pivot on the bracket portion
with a socket portion on a mirror carrier with intergrated
electrical routing straps for interconnecting an electrical routing
assembly like that of the first embodiment of FIGS. 99 102 with the
heater element.
FIG. 105 is an exploded perspective view of an eighth embodiment of
a vehicular mirror assembly having a mirror housing mounted to a
base adapted to be mounted to a vehicle, the mirror assembly
including a power assist device with a motor interconnected to a
shut-off circuit according to the invention.
FIG. 106 is a schematic view of the shut-off circuit of FIG.
105.
FIG. 107 is a circuit diagram of an embodiment of the shut-off
circuit of FIG. 105.
FIG. 108 is a circuit diagram of FIG. 107 showing the circuit in a
first state.
FIG. 109 is a circuit diagram of FIG. 107 showing the circuit in a
second state.
FIG. 110 is a circuit diagram of FIG. 107 showing the circuit in a
third state.
FIG. 111 is a circuit diagram of FIG. 107 showing the circuit in a
fourth state.
FIG. 112 is a schematic view of a driver seated within the vehicle
having a prior art externally-mounted rearview mirror, or in the
schematic view shows the mirror in a retracted position with
respect to the vehicle body and dashed lines indicate the driver's
field of view with respect to the retracted mirror.
FIG. 113 is a schematic view in a similar orientation to that shown
in FIG. 112 of the driver seated within a vehicle having a prior
art externally-mounted rearview mirror, wherein the schematic view
shows the mirror in an extended position with respect to the
vehicle body and dashed lines indicate the driver's field of view
with respect to the extended mirror and showing a blind spot
created adjacent to the driver's field of view.
FIG. 114 is a schematic view in a similar orientation to that shown
in the FIG. 112 of a driver seated within the vehicle comprising a
ninth embodiment of a vehicular rearview mirror assembly according
to the invention, wherein the schematic view shows the inventive
mirror in a retracted position with respect to the vehicle body and
dashed lines indicate the driver's field of view with respect to
the retracted mirror.
FIG. 115 is a schematic view in a similar orientation to that shown
in FIG. 112 of a driver seated within a vehicle having a vehicular
rearview mirror assembly according to the invention, wherein the
schematic view shows the inventive mirror in an extended position
with respect to the vehicle body and dashed lines indicate an
adjusted field of view with respect to the extended mirror.
FIG. 116 is a perspective view of the vehicle rearview mirror shown
schematically in FIGS. 114 115 in a retracted position.
FIG. 117 is a perspective view of the vehicle rearview mirror shown
schematically in FIGS. 114 115 in an extended position.
FIG. 118 is a front elevational view of the vehicle rearview mirror
of FIG. 116 in a retracted position.
FIG. 119 is a cross-sectional view of the vehicle mirror of FIG.
116 taken along lines 119--119 of FIG. 118.
FIG. 120 is a front elevational view of the vehicle rearview mirror
of FIG. 117 in an extended position.
FIG. 121 is a cross-sectional view of the vehicle mirror of FIG.
117 taken along lines 121--121 of FIG. 120.
FIG. 122 is a front elevational view of an alternative embodiment
of the vehicle mirror shown in FIGS. 114 117 in a retracted
position.
FIG. 123 is a cross-sectional view of the vehicle mirror of FIG.
122 taken along lines 123--123 thereof.
FIG. 124 is a front elevational view of the alternative embodiment
of the vehicle mirror shown in FIG. 122 in an extended
position.
FIG. 125 is a cross-sectional view of the vehicle mirror of FIG.
124 taken along lines 125--125 thereof.
FIG. 126 is a cross-sectional view of another embodiment of the
vehicle mirror according to the invention in a retracted
position.
FIG. 127 is a cross-sectional view of the embodiment of the vehicle
mirror shown in FIG. 126 in an extended position.
FIG. 128 is an exploded view of a tenth embodiment of a rearview
mirror assembly illustrating the major components thereof including
a drive assembly connecting a mirror assembly to a support bracket
with a pivot mechanism for rotating and an extension mechanism for
extending the mirror assembly relative to a vehicle.
FIG. 129 is a perspective view of an outer housing comprising a
portion of the pivot mechanism of FIG. 128.
FIG. 130 is a perspective view of the interior of the outer housing
of FIG. 129.
FIG. 131 is an exploded view of a ramp, a wave spring, and an
actuator sub comprising a portion of the pivot mechanism of FIG.
128.
FIG. 132 is a perspective view of the ramp of FIG. 131.
FIG. 133 is a perspective view of the wave spring of FIG. 131.
FIG. 134 is a perspective view of the interior of the actuator sub
of FIG. 131.
FIG. 135 is an exploded view of a spring, an actuator sub ring, and
a ring gear comprising a portion of the pivot mechanism of FIG.
128.
FIG. 136 is a perspective view of the interior of the actuator sub
of FIG. 131 showing the spring, the actuator sub ring, the ring
gear, and a C-ring installed therein.
FIG. 137 is a perspective view of the assembled pivot mechanism of
FIG. 128.
FIG. 138 is a perspective view of a portion of the drive assembly
of FIG. 128 related to the extend function.
FIG. 139 is a perspective exploded view of some of the components
shown in FIG. 137, including the motor according to the invention
with the cover removed in relation to the drive assembly.
FIG. 140 is a plan view of the motor assembly of FIGS. 138 and 139
with the extend output screw.
FIG. 141 is an end view of the rearview mirror assembly of FIG. 128
with the housing removed for clarity.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Several embodiments of a pivotably foldable and linearly extendable
mirror are described herein. The embodiments comprise a
functionality module comprising one or more of a powered-fold,
powered-extend mechanism; a powered-fold, manual-extend mechanism;
a manual-fold, powered-extend mechanism; a manual-fold,
manual-extend mechanism; a powered-fold mechanism; a powered-extend
mechanism; a manual-extend mechanism; and a manual-fold mechanism,
as more fully disclosed herein.
Many of the elements of the mirror are common to more than one
embodiment, and thus like numerals will be use to identify like
elements in the several embodiments, except where otherwise
indicated.
Referring now to the drawings and to FIGS. 1 4 in particular, a
first embodiment of a vehicular mirror assembly 10 is shown
comprising a mirror housing 12 pivotally and extendably mounted to
a base 14, and driven by a motive element such as a 12-volt DC
motor. The mirror housing 12 preferably carries a reflective
element, such as a mirror, as identified by reference number 16. It
will be understood that alternative and additional accessories for
the mirror housing 12, base 14, and reflective element 16 can be
included without departing from the scope of this invention. For
example, the reflective element 16 can also include a wide view
portion 18 as would be known to one skilled in the art. Other
optional accessories include illumination devices such as a turn
signal, or an assist light, and the like.
FIGS. 1 and 2 show the vehicular mirror assembly 10 located in an
unfolded, use position wherein the mirror housing 12 is pivoted
radially outwardly from the base 14 (i.e., adjacent the vehicle) so
that the reflective element 16 is positioned for viewing by an
occupant of the vehicle.
FIGS. 3 and 4 show the vehicular mirror assembly 10 located in a
folded, stored position wherein the mirror housing 12 is pivoted
radially inwardly toward the base 14 so that the reflective element
16 is stored adjacent to the vehicle and is less likely to be
damaged by events external to the vehicle, such as passers by,
other vehicles, carwashes, and the like.
FIG. 58 shows a vehicular mirror assembly 10 located in an
unfolded, extended, use position wherein the mirror housing 12 is
pivoted radially and extended linearly outwardly from the base 14
so that the reflective element 16 is positioned for viewing by an
occupant of the vehicle when an enhanced field of view is desired,
such as when the vehicle is towing a trailer.
A first embodiment of a pivot mechanism according to the invention
will now be described. Turning to FIG. 5, the base 14 is shown
comprising an upper portion 20 which functions as a cover and a
lower portion 22 which functions as a support bracket for both
mounting the base 14 to a vehicle and receiving a pivot mechanism
24. The pivot mechanism 24 is preferably fixedly mounted within the
upper and lower portions 20 and 22 of the base 14 and includes a
rotatable column which is mounted to the mirror housing 12 to
effect the pivotal movement of the mirror housing 12 relative to
the base 14.
Turning to FIG. 6, an underside 26 of the upper portion 20 of the
base 14 is shown in greater detail. In addition to several mounting
bosses 28 for receiving fasteners to mount the upper portion 20 to
the lower portion 22, the upper portion 20 also includes a recess
30 adapted to receive an upper portion of the pivot mechanism 24
and to journal the same therein. The recess 30 is surrounded by an
annular track 32 having a pair of diametrically opposed detents 34
having a generally trapezoidal configuration. The detents 34 are
adapted to engage the pivot mechanism 24 in a manner that will be
more fully described below.
FIG. 7 shows the upper and lower portions 20, 22, respectively, and
the pivot mechanism 24 in greater detail. Other than the specific
features of the upper portion 20 called out with respect to the
description of FIG. 6, the upper and lower portions 20 and 22 of
the base 14 to be of any suitable configuration to be both mounted
to a vehicle and to carry the mirror housing 12 for pivotal
movement via the pivot mechanism 24. In general, the upper and
lower portions 20 and 22 of the base 14 provide a housing for the
pivot mechanism 24.
The structure of the components making up the pivot mechanism 24
will now be described in greater detail with respect to FIG. 7. The
pivot mechanism 24 comprises a motor assembly 36, a pair of
transfer gears 38 and 40, a rotatable column 42, an output gear 44,
a release ring 46, a spring 48, a control ring 50 and upper and
lower bushings 52 and 54, respectively.
The motor assembly 36 can be any of several well-known DC motors as
would be known to one skilled in the art. It will be understood
that, although a DC motor having a heavy-duty motor rating would
have been used with prior art mirror pivoting devices, a DC motor
having lighter duty characteristics can be used herein as a result
of the pivoting force reduction mechanism embodied in the pivot
mechanism 24 as will be more fully described herein. Alternatively,
a motor rated the same as that used in the prior art can also be
employed herein as well with the additional incidental benefits of
lower power consumption and a longer motor life as a result of the
force-reducing mechanism of the invention. As to be seen from FIG.
7, the motor assembly 36 preferably has an output shaft 56 that is
rotatable upon any suitable signal and/or current applied to
terminals 58 of the motor assembly 36.
The transfer gears 38 and 40 can be any acceptable gear in any of a
number of well-known configurations for transferring the rotational
output of the shaft 56 of the motor assembly 36 to the output gear
44 of the pivot mechanism 24. An example shown, a simple worm makes
up the transfer gear 38 which, in turn, is meshed with the transfer
gear 40 (shown generally as a spool-type gear). In turn, the
transfer gear 40 can be operably interconnected with the output
gear 44.
The rotatable column 42 comprises an elongated body 60 having a
lower bearing portion 62 and an upper engagement portion 64
rotatably mounted thereto, separated by a radially-extending
shoulder 66. The upper engagement portion 64 of the elongated body
60 preferably has a discontinuous cross section, such as the
sprocket-type cross section shown in FIG. 7. In this embodiment,
the upper engagement portion 64 has an outer diameter and an inner
diameter. It will be understood that the discontinuous cross
section of the upper engagement portion 64 preferably functions as
a "key" for the release ring 46 and the control ring 50 as will be
more fully described below. The upper engagement portion 64 also
includes a diametrical bore 68 which is adapted to receive a pin 70
therethrough.
The output gear 44 comprises an annular body 72 having a peripheral
surface 74, preferably provided with gear teeth of a pitch and
diameter generally corresponding to that of the transfer gears 38
and 40. A central recess 76 is defined within the interior of the
annular body 72. Further, an upper surface of the annular body 72
includes a number of detents 78, preferably at spaced radial
locations thereon.
The release ring 46 comprises an annular body 80 having a central
recess 82. A lower portion of the annular body 80 preferably has an
outer diameter corresponding to that of the output gear 44. An
upper portion of the annular body 80 preferably has a
reduced-diameter neck portion 84 extending upwardly therefrom. The
lower portion of the annular body 80 has an underside surface with
indentations 86 preferably corresponding in spacing and alignment
with the detents 78 on the output gear 44. An inner wall defining
the central recess 82 preferably has a cross section adapted to be
received on the upper engagement portion 64 of the rotatable column
42 for slidable but non-rotatable engagement therewith.
The spring 48 can be any suitable biasing member for placing the
pivot mechanism 24 in tension. By way of example and not in
limitation of the invention, a coil spring is shown as the spring
48 in the drawings associated with this embodiment of the
invention. Substitute types of biasing members for the coil spring
include leaf springs, ramp springs, and the like. Preferably, the
spring 48 has a central recess 88 adapted to be received on the
upper engagement portion 64 in a slidable manner and adapted to
seat on the reduced-diameter neck portion 84 of the release ring
46.
The control ring 50 comprises an annular body 90 having a central
recess 92. An inner wall defining the central recess 92 preferably
has a cross section adapted to be received on the upper engagement
portion 64 of the rotatable column 42 for slidable but
non-rotatable engagement therewith. A lower portion of the annular
body 90 preferably has a reduced-diameter neck portion 94 of
similar configuration to the neck portion 84 of the release ring
46. The annular body 90 preferably extends radially outwardly to a
greater extent than the neck portion 94. An upper surface 96 of the
annular body 90 of the control ring 50 preferably includes a pair
of opposed grooves 98 having terminal ends which preferably define
a normal range of movement of the mirror housing 12 between the
retracted and extended positions with respect to the base 14. As
can be seen from FIG. 7, the grooves 98 extend inwardly from a
peripheral edge of the annular body 90, preferably having a radial
width generally corresponding to the detents 34 on the upper
portion 20 of the base 14. The grooves 98 also preferably have a
depth being slightly less than the vertical height of the detents
34.
The upper and lower bushings 52 and 54 are preferably any suitable
annular member for securing the pivot mechanism 24 within the
recess 30 in the upper portion 20 and a similar recess (not shown)
in the lower portion 22 of the base 14.
The assembly of the pivot mechanism 24 from the components 36 50
will now be described. The lower bushing 54 is mounted within the
suitable recess in the lower portion 22 of the base 14. The lower
bearing portion 62 of the rotatable column is placed within the
lower bushing 54 and is fixedly mounted to the lower portion 22 of
the base 14 such as with one or more conventional fasteners (not
shown). The transfer gear 38 is fixedly mounted on the output shaft
56 of the motor assembly 36 and the transfer gear 40 is mounted for
rotation within the lower portion 22 of the base 14. The motor
assembly 36 (with the attached transfer gear 38) is preferably
mounted within the lower portion 22 of the base 14 in a manner that
enmeshes the teeth of the transfer gear 38 with the teeth of the
transfer gear 40.
The output gear 44 is placed onto the upper engagement portion 64
of the rotatable column 42. It will be understood that, since the
central recess 76 of the output gear 44 has a smooth inner surface,
the output gear 44 can rotate freely with respect to the upper
engagement portion 64. The gear teeth on the peripheral surface 74
of the output gear 44 are preferably enmeshed with the teeth of the
transfer gear 40 when the output gear rests atop the shoulder 66 on
the rotatable column 42.
The release ring 46 is placed onto the upper engagement portion 64
so that the discontinuous central recess 82 of the release ring 46
is keyed for rotation with the sprocket-type cross section of the
upper engagement portion 64 of the rotatable column 42. In
addition, the indentations 86 on the underside of the release ring
46 preferably receive the corresponding detents 78 on the upper
surface of the output gear 44.
The spring 48 is placed onto the upper engagement portion 64 of the
rotatable column 42 so that a bottom surface of the spring 48 rests
on the annular body 80 of the release ring 46 and the
reduced-diameter neck portion 84 of the release ring 46 is received
within the central recess 88 of the spring 48.
The control ring 50 is placed onto the upper engagement portion 64
of the rotatable column 42 so that the reduced-diameter neck
portion 94 of the control ring 50 seats within the central recess
88 of the spring 48. In addition, the discontinuous central recess
92 of the control ring 50 is preferably keyed for rotation with the
sprocket-type cross-section section of the upper engagement portion
64 of the rotatable column 42.
Once these components are placed on the upper engagement portion 64
of the rotatable column 42, the control ring 50 is depressed
against the bias of spring 48 until an upper surface of the annular
body 90 of the control ring 50 traverses past the bore 68 located
in the upper engagement portion 64 of the rotatable column 42. Once
the control ring 50 is depressed beneath the bore 68, the shaft 70
is inserted within the bore 68 and the downward pressure on the
control ring 50 is released. The spring 48 attempts to return to
its unbiased position and bears the upper surface of the annular
body 90 of the control ring 50 against ends of the shaft protruding
from the bore 68. The assembly serves as a force-modifying device
by reducing the force between the detents 34 and the grooves 98,
thus reducing the force needed to rotate the mirror housing
relative to the base 14. The assembled pivot mechanism 24 can be
seen in FIG. 8.
The upper bushing 52 is placed within the recess 30 and the upper
end of the upper engagement portion 64 is passed through the recess
30 in the upper portion 20 of the base 14 where it is mounted,
preferably fixedly, to the mirror housing 12. Rotation of the upper
engagement portion 64 relative to the lower bearing portion 62 of
the rotatable column 42 causes rotation of the mirror housing 12
relative to the base 14, and vice versa.
With reference to the pivot mechanism 24 shown in FIG. 8, the
operation of the pivot mechanism 24 for pivotally moving the mirror
housing 12 with respect to the base 14 will now be described with
respect to FIGS. 9 14. FIGS. 9 11 are illustrative of a "normal
range of operation" condition in which the motor assembly 36 drives
the rotatable column 42 between the extended and retracted
positions. FIGS. 12 14 are illustrative of an "overtravel range of
operation" condition in which a user has manually pivoted the
mirror housing 12 either past the normal extended position or past
the normal retracted position and has thereby implicated the
overtravel accommodation features of the pivot mechanism 24.
The operation of the pivot mechanism 24 with respect to the normal
range of movement of the mirror housing 12 with respect to the base
14 will now be described with respect to FIGS. 9 11. In the normal
range of movement, the detents 34 are located within, but do not
contact, the grooves 98 on the control ring 50 as a result of the
bias of the pin 70 against the non-grooved portion of the upper
surface 96 of the control ring 50. In this manner, the pin 70 holds
the control ring 50 a sufficient downward distance from the detents
34 on the upper portion 20 of the base 14 to prevent the detents 34
from contacting the surfaces making up the grooves 98 on the
control ring 50. Thus, the motor assembly 36 does not need to
overcome any friction between the control ring 50 and the detents
34 throughout the normal range of movement of the mirror housing 12
with respect to the base 14.
For example, to impart motorized movement of the mirror housing 12
with respect to the base 14 via the pivot mechanism 24, a suitable
signal is sent to the terminals 58 on the motor assembly 36 which
rotates the output shaft 56 in the desired direction. This, in
turn, imparts rotary motion to the first transfer gear 38 and to
the second transfer gear 40. The rotation of the second transfer
gear 40 rotates the output gear 44 of the pivot mechanism 24 which,
in turn, rotates the release ring 46 as a result of the engagement
of the detents 78 on the output gear 44 with the indentations 86 of
the release ring 46. Since the central recess 82 of the release
ring 46 is keyed for rotation with the upper engagement portion 64
of the rotary column 42, the rotatable column 42 rotates with the
release ring 46 and thus provides the appropriate rotation to the
mirror housing 12 attached thereto.
The limits of this rotational movement of the mirror housing 12
with respect to the base 14 via the pivot mechanism 24 are defined
by the position of the detents 34 of the upper portion 20 of the
base 14 with respect to the terminal ends of the grooves 98 on the
control ring 50. Although the detents 34 do not touch the surfaces
making up the grooves 98 on a control ring 50 as a result of the
positioning of the pin 70, the detents 34 do contact the control
ring 50 at the innermost and outermost limits of the normal range
of travel of the mirror housing 12 with respect to the base 14.
Once a corresponding detent 34 contacts a terminal end of the
grooves 98, the rotation of the rotatable column 42 stops.
Preferably, the motor assembly 36 is not sufficiently strong (i.e.,
has sufficient torque) to force the control ring 50 to overrotate
against the end of the grooves 98.
In addition to the motorized travel of the mirror housing 12 with
respect to the base 14 as defined by the pivot mechanism 24, the
inventive pivot mechanism 24 described herein also allows a manual
override of the motorized travel permitted by the motor assembly
36. For example, when a user grasps the mirror housing 12 and
manually rotates the mirror housing 12 with respect to the base 14,
the pivot mechanism 24 described herein permits this movement
without damage to the interior components thereof.
As would be apparent to one skilled in the art, manual rotation of
an output gear (such as output gear 44) with respect to a driven
gear (such as the output shaft 56 and its associated transfer gears
38 and 40) often causes the gear assembly to lock up. In this case,
the pivot mechanism 24 includes a clutch-type mechanism that
releases the output gear 44 from the release ring 46 to allow this
manual rotation. As can be seen from the drawings, when a user
manually rotates the mirror housing 12, the upper engagement
portion 64 of the rotatable column 42 rotates with the mirror
housing 12 in response to the manual rotation imparted by the user.
In this case, the output gear 44 locks against the second transfer
gear 40 and does not rotate. However, since the release ring 46 is
keyed for motion with the upper engagement portion 64 of the
rotatable column 42, the release ring 46 continues to rotate,
causing the indentations 86 to release from engagement with the
detents 78, thus causing separation of the release ring 46 from the
output gear 44. The bottom surface of the release ring 46 thereby
travels along the top surfaces of the detents 78, rotating the
release ring 46 with respect to the output gear 44.
Depending upon the position of the mirror housing 12 with respect
to the base 14, one of three scenarios occurs.
First, if the mirror housing 12 is within the normal range of
movement with respect to the base 14, the mirror housing 12 can be
rotated easily with respect to the base 14 since the detents 34 on
the upper portion 20 of the base 14 are withheld from contact from
the control ring 50 because of their location within the grooves 98
thereof. This feature is illustrated in FIGS. 9 11 by gap 106 shown
between control ring 50 and the detents 34 on the base 14.
Second, if the mirror housing 12 is at the end (i.e., either the
innermost or outermost) of the normal range of movement of the
mirror housing 12 with respect to the base 14, additional force
imparted by the user causes the detents 34 to be biased against the
corresponding terminal end of the grooves 98 on the control ring 50
and causes the detents 34 to bias the control ring 50 downwardly
against the force of the spring 48. In this manner, the control
ring 50 is urged downwardly and the detents 34 now frictionally
engage the upper surface of the control ring 50. When the mirror
housing 12 is at rest at the innermost or outermost range of
travel, backlash (i.e., unintended movement of the mirror housing
12 with respect to the base 14) is prevented by the abutment of the
detents 34 against the corresponding end of the grooves 98.
Third, once the mirror housing 12 is urged past the end of the
normal range of movement of the mirror housing 12 with respect to
the base 14 and the detents 34 are now located on the upper surface
of the control ring 50, rotation of the mirror housing 12 with
respect to the base 14 is now more difficult because the user must
overcome the bias of the spring 48 against the detents 34 through
the control ring 50 (i.e., the pivoting force reduction mechanism
of the pin 70 as in the first scenario is no longer in effect).
As can be seen, a motor assembly 36 having lighter duty
characteristics (i.e., a lower characteristic torque) can be used
because the motor assembly 36 does not have to overcome the
friction caused by the abutment of the control ring 50 against the
detents 34 during the normal range of movement of the mirror
housing 12 with respect to the base 14.
A second embodiment of the pivot mechanism 24 is shown in FIGS. 15
20. It will be understood that common elements between the
embodiment shown in FIGS. 1 14 and the second embodiment shown in
FIGS. 15 20 are referred to with common reference numerals and a
duplicate description of the second embodiment of FIGS. 15 20 need
not be provided in great detail. Rather, it will be understood that
the differentiating features of the second embodiment of FIGS. 15
20 mainly relate to the provision of the motor assembly and
transfer gears within the interior of the rotatable column 42
rather than adjacent thereto as in the first embodiment of FIGS. 1
14. In addition, the "keying" of the rotation of the elements to
the lower portion 22 of the base 22 is caused by the engagement of
keys 100 of components 46 and 50 within the grooves 102 of the
lower portion 22 of the base 14. The function of the pin 70 is
accomplished by a split ring retainer 70 which snaps into a groove
104 in the lower portion 22 of the base 14 to compress the spring
48 and perform the force-reducing function of a force-modifying
device during the normal range of movement. Otherwise, the
structure, assembly and operation of the second embodiment of FIGS.
15 20 is virtually identical to that described with respect to the
embodiment shown in FIGS. 1 14.
FIG. 21 illustrates a third embodiment of the pivot mechanism 120.
The pivot mechanism 120 is preferably fixedly mounted within the
base 14 and includes a rotatable column hereinafter described which
is mounted to the mirror housing 12 to effect the pivotal movement
of the mirror housing 12 relative to the base 14.
The pivot mechanism 120 comprises an outer housing 122 and a base
370 which enclose a ramp 150, a wave spring 170, an actuator sub
180, a motor housing 260, a motor 300, and gear assemblies 310,
360. Referring also to FIGS. 22 and 23, the outer housing 122 is a
generally cylindrically-shaped body comprising a cylindrical wall
124 and a collar 126 connected to the cylindrical wall 124 by an
annular wall 128 and coaxial therewith. The annular wall 124
extends orthogonally inwardly from the cylindrical wall 124 to the
collar 126. Referring to FIG. 23, the inner surface of the annular
wall 128 is provided with a pair of diametrically-opposed inner
bosses 142 extending downwardly from the annular wall 128. The
collar 126 comprises a generally ring-shaped structure defining an
circular opening 130. The cylindrical wall 124 defines a
cylindrical chamber 144. Extending orthogonally outwardly from the
cylindrical wall 124 at an opposite end from the collar 126 is a
base ring 122 circumscribing the cylindrical wall 124. The base
ring 122 is provided with a plurality of mounting bosses 134 spaced
above the periphery of the cylindrical wall 124 and having a
mounting bore 140 extending therethrough generally parallel to the
longitudinal axis of the outer housing 122. Extending downwardly
from the base ring 132 are a pair of diametrically-opposed mounting
pegs 136 generally parallel to the longitudinal axis of the outer
housing 122, and a pedestal 138 for holding a mounting bearing
(later described with reference numeral 350) into place.
Referring now to FIGS. 24 26, a ramp 150 is a ring-like body
comprising a pair of diametrically-opposed thin ring segments 152
in alternating juxtaposition with a pair of diametrically-opposed
raised segments 154. The raised segments 154 transition to the thin
ring segments 152 through terminal ends defined by a first inclined
face 156 and a second inclined face 158. The thin ring segments 152
and the raised segments 154 define a circular inner wall 155
defining a generally circular center opening 162. Regularly spaced
along the inner wall 155 are a plurality of notches 160. In the
preferred embodiment shown in FIG. 24, six notches 160 are shown in
diametrically-opposed pairs. One pair of notches 160 bisect the
raised segments 154, the remaining notches 160 are formed at each
end of the thin ring segments 152.
A wave spring 170 is a generally helical spring formed of a flat
ribbon of metal, preferably spring steel having alternating crest
portions 172 and trough portions 174. The spring 170 is formed so
that the trough portions 174 of one coil contact the trough
portions 174 of the adjoining coil. Preferably, the trough portions
174 in contact with one another are fixedly connected, such as by
spot welding. The spring 170 defines a circular center opening
176.
An actuator sub 180 is a generally cylindrically-shaped body
comprising a generally cylindrical lower housing 182 and a
generally cylindrical upper housing 184. The lower housing 182
comprises a lower cylindrical wall 186 transitioning to an
inwardly-extending annular wall 188 which, in turn, transitions to
an upper cylindrical wall 192 of the upper housing 184. The lower
cylindrical wall 186 is provided with a plurality of peripheral
slots 190 spaced thereabout at an opposite end from the upper
housing 184. The upper cylindrical wall 192 transitions to an
annular top wall 194 having a depending inner peripheral wall 196
defining a circular opening 198. The upper cylindrical wall 192 is
provided with a plurality of regularly-spaced ribs 200 extending
longitudinally along the upper cylindrical wall 192 from the
annular wall 188. The ribs 200 are adapted to slidably engage the
notches 160 in the ramp 150 when the upper housing 184 is inserted
through the center opening 162. A plurality of seats 202 are spaced
regularly around the upper housing 184 at the inner face of the top
wall 194 and the upper cylindrical wall 192. Preferably, the seats
202 are spaced at 120 degrees around the periphery of the upper
cylindrical wall 192. Upper housing sockets 204 comprise circular
apertures through the top wall 194 at regularly-spaced intervals.
Preferably, the sockets 204 are spaced at 120 degrees around the
top wall 194.
As shown in FIG. 38, the wave spring 170 is placed over the upper
housing 184 so that the upper housing 184 extends through the
center opening 176. The ramp 150 is then placed over the upper
housing 184 to abut the wave spring 170 so that the upper housing
184 extends through the center opening 162. The wave spring 170
will urge the ramp 150 in a direction away from the annular wall
188.
Referring to FIG. 27, a plurality of actuator sub ring channels 206
comprise longitudinal channels in the inner portion of the lower
cylindrical wall 186 generally parallel to the longitudinal axis of
the actuator sub 180. The channels 206 extend along the lower
cylindrical wall 186 from the open end of the actuator sub 180. In
the preferred embodiment, three channels 206 are spaced at 120
degrees along the interior of the lower cylindrical wall 186. A
circumferential C-ring channel 208 extends around the periphery of
the lower cylindrical wall 186 along the inner surface thereof
adjacent the opening to the actuator sub 180.
Referring now to FIGS. 28 29, an actuator sub ring 210 is a
generally ring-like body comprising an annular wall 212 defining a
circular opening 220. Slots 214 are cut into the ring 210 at
regularly spaced intervals, preferably 90 degrees, to define
segments 216. A plurality of outwardly-extending ribs 218 is spaced
about the outer periphery of the ring 210, preferably at 120
degrees. The actuator sub ring 210 is adapted to be slidably
inserted into the actuator sub 180 and the ribs 218 are adapted to
be slidably inserted into the actuator sub ring channels 206 as
shown in FIG. 29.
A ring gear 230 comprises an annular body 232 defining a circular
opening 238. An upper surface of the annular body 232 includes a
plurality of bosses 234, preferably at regularly-spaced radial
locations thereon. In the preferred embodiment, four bosses 234 are
spaced at an interval of 90 degrees. The inner surface of the
annular body 232 is provided with a plurality of teeth 236 in
longitudinal alignment with the axis of the ring gear 230. The
bosses 234 are adapted to slidably engage the slots 214 in the
actuator sub ring 210. The ring gear 230 is adapted to be slidably
inserted into the actuator sub 180, as shown in FIG. 29.
As also shown in FIG. 29, a spring 240 comprises a generally
conventional helical spring adapted to be slidably inserted into
the actuator sub 180 and abut the annular wall 188 and of the
actuator sub ring 210. A conventional C-ring 250 is adapted to be
retained within the C-ring channel 208 in a generally conventional
manner. As shown in FIG. 29, the spring 240 is slidably inserted
into the actuator sub 180 to abut the annular wall 188. The
actuator sub ring 210 is then inserted into the actuator sub 180 so
that the ribs 218 slidably communicate with the actuator sub ring
channels 206, to abut with the slots 214 extending away from the
spring 240. The ring gear 230 is then slidably inserted into the
actuator sub 180 so that the bosses 234 engage the slots 214. The
spring 240, the actuator sub ring 210, and the ring gear 230 are
retained in the actuator sub 180 by compressively inserting the
C-ring 250 into the C-ring channel 208.
Referring now to FIGS. 30 and 31, a motor housing 260 is a hollow,
generally cylindrically shaped body, comprising a housing body 262
and a motor cradle 264. The housing body 262 comprises a lower
cylindrical wall 266 transitioning, in part, to a chord wall 268
and a segment wall 270 orthogonal thereto. The lower cylindrical
wall 266 is interrupted by a gear opening 272 at a lower portion
thereof adjacent the segment wall 270. The lower cylindrical wall
266 terminates in an outwardly-extending lower annular wall
274.
The motor cradle 264 comprises a motor yoke 276 attached to an
upper cylindrical wall 278. The upper cylindrical wall 278 extends
longitudinally from an upper annular wall 292 extending inwardly
from the lower cylindrical wall 266. The motor yoke 276 comprises a
pair of diametrically-opposed yoke supports 280 extending
longitudinally from the upper cylindrical wall 278 and joined by a
diametrically-extending crosspiece 282. Extending outwardly from
the crosspiece 282 and an outer portion thereof are a pair of
generally parallel, spaced-apart pegs 284. The crosspiece 282 is
provided near each end with an arcuate cutout 286. The crosspiece
282 is also provided with a circular yoke aperture 288 in coaxial
alignment with the housing body 262.
Diametrically opposite the chord wall 268 is an extension wall 290
extending longitudinally from the upper cylindrical wall 278,
terminating in a curved section 294 which acts as a strain relief
for motor wires. The lower annular wall 274 is provided with a pair
of diametrically-opposed mounting posts 296 in generally parallel
alignment with the longitudinal axis of the housing body 262. The
segment wall 270 is provided with an output shaft seat 298
penetrating therethrough. The inner surface of the lower
cylindrical wall 266 is provided with diametrically-opposed pairs
of parallel, longitudinally spaced-apart motor mounting ribs
299.
A motor 300 comprises a generally conventional 12-volt DC electric
motor suitable for the use described herein. Preferably, the motor
300 comprises a shaft 306 to which is attached a worm gear 302. At
an end opposite the worm gear 302 is a bearing 304. The motor 300
is generally cylindrical in the overall configuration, but having
at least one motor casing face 308.
Referring to FIGS. 32 and 33, an intermediate shaft assembly 310
comprises a secondary gear 312, a primary gear 328, a spring 338,
and a spring retainer 340. The secondary gear 312 comprises a
helical gear portion 314 (such as a worm), a wheel portion 316 in
abutment thereto and having a clutch drive surface 318, with a
major shaft 320 extending from the clutch drive surface 318 coaxial
therewith, a coaxially-aligned shaft extension 322 extending from
the major shaft 328, and a minor shaft 326 extending from the
helical gear portion 314 in axial alignment with the major shaft
328 and shaft extension 322.
Referring also to FIG. 35, the primary gear 328 (e.g., a helical
gear) comprises a toothed portion 330 terminating in a cylindrical
wall 332. Opposite the cylindrical wall 332, the toothed portion
330 terminates in a clutch driven surface 334 having a shaft
aperture 335 extending axially therethrough. The primary gear 328
encloses a spring receptacle 336 for slidable insertion of a
conventional helical spring 338. The spring 338 is retained in the
spring receptacle 336 by the spring retainer 340. The spring
retainer 340 comprises an inner hub 342 transitioning to a flange
344 which, in turn, transitions to an outer hub 346. The spring
retainer 340 is provided with a shaft aperture 348 coaxially
therethrough. The shaft extension 322 and the minor shaft 326 are
journaled into bearings 350 for rotational movement therewithin.
The clutch driving surface 318 and the clutch driven surface 334
together comprise a force-modifying device which will enable
relative rotation of the two surfaces 318, 334 when a predetermined
frictional force has been exceeded.
An output shaft 360 is an elongated body comprising a drive gear
362 and a driven gear 364, in spaced-apart relationship having a
shaft 366 extending therethrough in coaxial alignment
therewith.
Referring also to FIG. 34, the base 370 is a generally
circular-shaped body comprising an annular portion 372 and a floor
portion 374. The annular portion 372 transitions to the floor
portion 374 through a downwardly depending annular wall 376.
Extending upwardly from the center of the floor portion 374 is a
worm gear housing 378 for surrounding the motor worm and supporting
the motor 300 comprising a generally semi-cylindrical
upwardly-extending wall 384 coaxial with the base 370 and defining
a worm gear cavity 386. The wall 384 is provided with a side
opening 388. The floor of the worm gear cavity 386 is provided with
a circular axle seat 390 in coaxial alignment with the wall
384.
Adjacent the worm gear housing 378, an output shaft housing 380 is
formed integrally with the floor portion 374 by a downwardly
depending curved wall 392 defining an output shaft cavity 394. The
wall 392 is provided with a side opening 396. The floor of the
cavity 394 is provided with a circular axle seat 398 in coaxial
alignment with the wall 392.
In operable juxtaposition with the side openings 388, 396 is an
intermediate shaft assembly housing 382 formed in the floor portion
374 by a downwardly depending housing wall 400 defining an
intermediate shaft assembly cavity 402. The intermediate shaft
assembly housing 382 is provided with a first bearing wall 404
adjacent a first end thereof, and a second bearing wall 406
adjacent a second end thereof. The first bearing wall 404 is
provided with an arcuate first shaft opening 408. The second
bearing wall 406 is provided with an arcuate second shaft opening
410. A first bearing seat 412 is formed at the first end of the
intermediate shaft assembly cavity 402 by the first bearing wall
404. A second bearing seat 414 is formed at the second end of the
intermediate shaft assembly cavity 402 by the second bearing wall
406.
A pair of diametrically-opposed mounting post sockets 416 are
provided in the floor portion 374 and adapted for slidable
communication with the mounting posts 296 of the motor housing 260.
A pair of diametrically-opposed mounting peg sockets 420 are
provided in the annular portion 372 and adapted for slidable
communication with the mounting pegs 136 of the outer housing 122.
A plurality of mounting bores 418 are provided through the annular
portion 372 for coaxial alignment with the mounting bores 140 of
the outer housing 122.
As shown in FIGS. 35 37, the worm gear shaft 306 is journaled into
the axle seat 390. The intermediate shaft assembly 310 is retained
in the intermediate shaft assembly cavity 302 by journaling the
shaft extension 322 and the minor shaft 326 into the bearings 350
which are retained in the bearing seats 412, 414, with the shaft
extension 322 and the minor shaft 326 extending through the shaft
openings 408, 410. As so assembled, the primary gear 328 operably
engages the worm gear 302 so that rotation of the worm gear 302
urges the primary gear 328 into horizontal rotation as shown in
FIG. 39.
The output shaft 366 is journaled into the axle seat 398 so that
the drive gear 362 occupies the output shaft cavity 394 and
operably engages the gear portion 314 of the intermediate shaft
assembly 310. The output shaft 366 adjacent the driven gear 364 is
journaled into the output shaft seat 298 in the motor housing 260
to operably engages the ring gear 230. As so assembled, rotation of
the worm gear 302 will urge the horizontal rotation of the primary
gear 328. Frictional engagement of the clutch drive surface 318
with the clutch driven surface 334 will urge the rotation of the
gear portion 314. Rotation of the gear portion 314 will urge the
drive gear 362 and the driven gear 364 into rotation. The rotation
of the driven gear 364 will urge rotation of the ring gear 230 as
shown in FIG. 39.
The pivot mechanism 120 is assembled as shown in FIGS. 21, 36, and
38. The wave spring 170 is inserted over the upper housing 184 of
the actuator sub 180. The ramp 150 is then inserted over the upper
housing 184 of the actuator sub 180 to abut the wave spring 170 so
that the raised segments 154 extend axially away from the lower
housing 182. The spring the 240, the actuator sub ring 210, and the
ring gear 230 are assembled into the lower housing 182 of the
actuator sub 180 as previously described and retained therein with
the C-ring 250. The assembled actuator sub 180 is then inserted
into the outer housing 122 so that the upper housing 184 extends
through the opening 130 and the actuator sub 180 is in slidable
communication with the outer housing 122 for rotational movement
therewithin.
The motor 300 is inserted into the motor housing 260 so that the
bearing 304 is retained in the yoke aperture 288. The motor housing
260 is then inserted through the C-ring 250, the spring 240, the
ring gear opening 238, and the actuator sub ring opening 220 into
the assembled actuator sub 180. The worm gear 302, the intermediate
shaft assembly 310, and the output shaft 360 are assembled into the
base 370 as previously described, and the base 370 is then
assembled to the outer housing 122 so that the mounting posts 296
of the motor housing 260 are inserted into the mounting post
sockets 416 of the base 370, and the mounting pegs 136 of the outer
housing 122 are inserted into the mounting peg sockets 420 of the
base 370. As so assembled, the motor housing 260, the motor 300,
and the outer housing 122 will be fixedly attached to the base 370.
The actuator sub 180 can rotate within the outer housing 122
between the outer housing 122 and the motor housing 400.
As shown in FIG. 39, actuation of the motor 300 will turn the worm
gear 302, which will urge rotation of the primary gear 328. The
frictional engagement of the clutch driven surface 334 with the
clutch drive surface 318 will urge rotation of the helical gear
portion 314. This will urge rotation of the drive gear 362 and the
driven gear 364. Rotation of the driven gear 364 will then urge
rotation of the ring gear 230. The engagement of the ring gear
bosses 234 with the slots 214 in the actuator sub ring 210 will
urge the rotation of the actuator sub 180. Thus, the upper housing
184 will rotate relative to the outer housing 122. With the outer
housing 122 operably connected to the mirror housing 112, the
mirror housing 112 will be selectively moved inwardly or outwardly
of the vehicle.
If the mirror assembly 110 reaches its fully extended or retracted
position before the motor 300 has stopped turning, further rotation
of the actuator sub 180 will be prevented. This will prevent
further rotation of the output shaft 360 and the helical gear
portion 314. The frictional engagement of the clutch drive surface
318 with the clutch driven surface 334 will be overcome so that the
clutch driven surface 334 will continue to rotate relative to the
clutch drive surface 318 until the motor 300 no longer turns.
Similarly, if the mirror assembly 112 is forcibly moved from an
extended position to a retracted position, such as would occur if
the mirror assembly 112 strikes an immovable object, the ring 210
is separated from engagement with ring 230 because the output shaft
360 is locked against manual rotation. The ring 210 can ride
against the underside of the ring 230 against the bias of the
spring 240 until the detents 234 re-engage with the slots 214 on
the ring 210 and the motor 300 can once again drive the rotation of
the mirror housing 112.
The herein-described invention provides a robust, compact pivot
assembly for selectively pivoting a vehicular mirror assembly to an
extended or a retracted position. The unique slip clutch enables
the motor powering the pivot assembly to continue to operate after
the mirror assembly has reached its fully extended or fully
retracted position without the increased current load and heat
generation otherwise experienced if the motor were to attempt to
operate the gearing that is prevented from rotating. Furthermore,
the slip clutch enables the mirror to be forcibly extended or
retracted without damaging the gears or the motor, thus extending
the life of the pivot assembly. The use of the slip clutch also
avoids the use of sophisticated and expensive electronics for
sensing an increase in load on the motor, such as would occur when
the mirror assembly reaches its fully extended or retracted
position, and turning off the motor in response.
FIG. 41 illustrates a fourth embodiment of a vehicle mirror 510
having both a power fold and a power extend function according to
the invention. The vehicle mirror 510 comprises a mirror assembly
512 and is mounted to a vehicle by a support bracket or arm 514.
Referring to FIG. 42, the mirror assembly 512 is connected to the
support arm 514 by a drive assembly or transmission 515, which is
used to rotate the mirror assembly between folded and unfolded
positions and extend the mirror assembly between retracted and
extended positions.
Referring to FIGS. 41 44, the mirror assembly 512 comprises a
mirror housing 516 in which is received a mirror bracket 518 that
supports a mirror drive 520 for adjusting the position of the
mirror 522 mounted to the mirror drive 520. The mirror drive 520
and mirror 522 are well known and will not be described in further
detail.
Referring specifically to FIG. 43, the mirror bracket 518 comprises
a generally planar upper face 528 on which the mirror drive 520 is
mounted. A C-shaped flange 530 extends away from the planar face
528 and defines a forward-facing channel 532. A laterally extending
plate 534 extends from the lower end of the flange 530.
Referring specifically to FIG. 44, slots 536 are formed in the
lower wall of the flange 530. Tabs 538 extend from the lower edge
of the flange 530 and are adjacent the slots 536. A catch 540
extends laterally from the planar face 528 on the side opposite the
mirror drive 520 and has a U-shaped notch 542.
Referring to FIGS. 41 and 42, the support arm 514 comprises a
shoulder 548 adapted to mount to the vehicle and a base 550
extending laterally from the shoulder. The base 550 has a generally
flat upper surface 552 from which extend a series of radially
spaced projections 554, with the intervening spaces forming detents
556. An opening 558 is located at the center of the projections 554
and extends through the base 550.
Referring to FIGS. 42 and 45 46, the drive assembly 515 comprises a
drive screw 562 coupled to an electric motor 564, which rotates the
drive screw 562 about the longitudinal axis of the drive screw 562.
An internally threaded drive nut 566 is threadably received on the
drive screw 562 and comprises a pin 568 extending laterally from
the drive nut 566 along an axis that is perpendicular to the
longitudinal axis of the drive screw 562 adapted to form a linkage
with the catch 540.
A detent assembly 570 mounts the electric motor 564 and a first
linkage such as a guide bracket 590 to the base 550 of the support
arm 514. The detent assembly 570 comprises an axle 572, a coil
spring 574, and a spur gear 576. The axle 572 has an end plate 578
on one end and a cap 580 on the other end. Spur gear 576 comprises
teeth 577 disposed about its periphery, a central opening 582, and
multiple dogs 584 extending downwardly from the bottom surface of
the spur gear 576. The dogs 584 are complementary in shape to the
detents 556 on the base upper surface 552.
The drive assembly 515 further comprises a rack gear 590 and a
guide bracket 592. The rack gear 590 comprises a rail 594 having a
series of teeth 596 on an inner surface thereof sized to match with
the teeth 577 of the spur gear 576. The rail 594 terminates in a
tab 598 having a notch 600.
The guide bracket 592 comprises a main plate 604 from which extends
a mounting tab 606 having an opening 608 for coupling the guide
bracket 592 to the axle 572 of the detent assembly 570. The
mounting tab 606 supports the electric motor 564. A limit flange
610 extends laterally from an upper end of the plate 604 and ends
at a post 612, which transitions into a guide flange 614 having a
slot 616 formed therein.
A slightly V-shaped cam 618 comprising upper and lower fingers 620,
622 is mounted to the post 612 by a pin 624 received within the
post 612. A cam surface 626 is formed between the upper and lower
fingers 620, 622. When the cam 618 is mounted to the post 612, the
lower finger 622 is aligned with the slot 616. A limit switch 630
is mounted to post 612 such that the switch overlies the notch
542.
When the drive assembly 515 is mounted to the base 550, the coil
spring 574 is mounted on the axle 572, the axle 572 is inserted
upwardly through the opening 558, the spur gear 576 is mounted to
the axle 572 adjacent the upper surface 552, and the axle 572 is
inserted through the opening 608 so that the cap 580 abuts the
upper surface of the mounting tab on the guide bracket 592. The
coil spring lower end will abut the axle end plate 578, the coil
spring upper end will abut an underside of the base top surface
552, and the dogs 584 will be received within the detents 556. In
such an orientation, the coil spring 574 draws the spur gear 576
toward the base top surface 552 to comprise a force-modifying
device, and the spur gear can only be rotated relative to the base
opening 558 by overcoming the spring force of the coil spring 574
such that the dogs 584 ride up and over the adjacent projections
554 and are received within the next radially positioned detents
556.
As assembled, the teeth 596 of the rack gear 590 mesh with the spur
gear teeth 577 and the rail 594 rests on the tab 606. The electric
motor 564 is sandwiched between the main plate 604 of the guide
bracket and the mirror bracket 518 such that any rotation of the
electric motor will result in a corresponding rotation of the
mirror bracket 518.
For convenience, the operation of the vehicle mirror 510 will be
described beginning with the mirror 510 in the initially unfolded
and retracted position as illustrated in FIGS. 47 49. In this
position, the pin 568 of the drive nut 566 is received within the
notch 600 of the rack gear 590, and the drive screw 562 has been
rotated by the electric motor 564 a sufficient amount that the
drive nut 566 is positioned longitudinally along the drive screw
562 such that the pin 568 lies beneath the cam surface 626 formed
by the upper and lower fingers 620, 622 and in alignment with the
slot 6116. The lower finger 622 is rotated exteriorly of the slot
616, and the upper finger 620 is received within the notch 542 on
the catch 540 of the mirror bracket 518. The upper finger 620 is
also spaced from the switch 630, leaving the switch 630 in its
naturally open state.
From the initial unfolded and retracted position as illustrated in
FIGS. 47 49, the reverse operation (counter-clockwise rotation of
the drive screw 562 as seen in FIG. 49) of the electric motor 564
will ultimately cause the mirror to rotate from the unfolded
position to the folded position as illustrated in FIGS. 50 53, and
the forward operation (clockwise rotation as seen in FIG. 49) of
the electric motor will initially transition the drive nut 566 from
coupling with the rack gear 590 to coupling with the mirror bracket
518 as illustrated in FIGS. 54 57 and ultimately cause the mirror
assembly 512 to extend from the retracted position to the extended
position as illustrated in FIGS. 58 61. The reverse operation of
the electric motor 564 results in the drive nut 566 moving towards
the electric motor 564 and the forward operation of the electric
motor 564 results in the drive nut 566 moving away from the
electric motor 564.
Referring to FIGS. 50 53, the movement of the mirror assembly 52
from the unfolded to the folded position will be described in
further detail. Upon the reverse operation of the electric motor
564, the drive nut 566, whose pin 568 is still received within the
notch 600, is drawn toward the electric motor 564, which, in turn,
urges the rack gear 590 toward the shoulder 548 of the support arm
514. If the spur gear 576 were free to rotate and not releasably
constrained by the detent assembly 570, the urging of the rack gear
590 toward the shoulder 548 would rotate the spur gear 576 relative
to the base 550 in a direction that would rotate the mirror housing
516 forwardly, instead of rearwardly as desired. However, since the
detent assembly 570 does releasably fix the spur gear 576 to the
base 550, for the rack gear 590 to rotate the spur gear 576, the
force applied by the rack gear 590 must overcome the compressive
force of the coil spring 574, which it does not. Since the force
applied by the rack gear 590 to the spur gear 576 is not enough to
overcome the coil spring 574, the rack gear 590 will instead
traverse the exterior of the spur gear 576, causing the rack gear
590 to rotate rearwardly carrying with it the electric motor 564
and, thus, the mirror bracket 518 to rotate the mirror assembly 512
into the folded position.
Referring specifically to FIG. 53, when the drive screw 562 is
rotated to effect the longitudinal movement of the drive nut 566
relative to the drive screw 562, the pin 568 is retained within the
notch 600 by the limit flange 610. The limit flange 610 acting on
the pin 568 prevents the nut 566 from rotating with the drive screw
562 as it naturally would instead of traversing along the drive
screw 562 as desired. The combination of the notch 600 and the
limit flange 610 effectively limits or prevents the relative
rotation of the drive nut 566 to the drive screw 562, which causes
the drive nut 566 to traverse the drive screw 562 upon the rotation
of the drive screw 562.
To return the mirror assembly 512 from the folded position to the
unfolded position, the electric motor 560 is operated in a forward
direction causing the rack gear 590 to once again traverse the
exterior of the spur gear 576 and rotate in a forward direction,
thereby rotating the mirror assembly 512 from the folded to the
unfolded position. The forward and reverse operation of the
electric motor can therefore be used to cycle the mirror housing
512 between the folded and unfolded positions as described.
Referring to FIGS. 47 and 54 57, the transition of the drive nut
566 from coupling with the rack gear 590 to coupling with the
mirror bracket 518 for initiating the extension and retraction of
the mirror assembly 512 will be described in further detail. As
previously described, in the unfolded and retracted position as
illustrated in FIG. 47, the pin 568 of the drive nut 566 is
received within the notch 600 of the rack gear 590 to couple the
drive nut 566 to the rack gear 590. However, the further forward
operation of the drive screw 562 will not yield an extension of the
mirror assembly 512, since the drive nut 566 is not directly
coupled to the mirror bracket 518 or indirectly coupled to the
mirror bracket through another structural item such as the guide
bracket 592. Therefore, the drive nut 566 must be coupled to the
mirror bracket 518 to effect the movement of the mirror assembly
512 from the retracted position to the extended position.
The forward operation of the drive screw 562 accomplishes the
uncoupling of the drive nut 566 from the rack gear 590 and the
coupling of the drive nut 566 to the mirror bracket 518. When the
mirror assembly 512 is in the unfolded and retracted position
illustrated in FIG. 47, the pin 568 is aligned with the slot 616 in
the guide bracket 592. Since the pin 568 is no longer rotationally
constrained by the limit flange 610, the, continued forward
operation of the drive screw 562 will result in the drive nut 566
rotating along with the drive screw 562 instead of longitudinally
traversing the drive screw 562 until the pin 568 is received within
the notch 542 of the catch 540 extending from the mirror bracket
518 to couple the drive nut 566 to the mirror bracket 518. As the
drive nut 566 rotates with the drive screw 562, the pin 568 follows
the cam surface 626 of the cam 618 causing the cam 618 to rotate,
resulting in the lower finger 622 entering the slot 616 and the
upper finger 620 moving out to the notch 542 and activating the
limit switch 630 to indicate that the drive assembly 515 is now
positioned for extension and retraction of the mirror assembly
512.
It should be noted that for convenience and to simplify the
description of the invention, the mirror assembly is described as
being in the unfolded and retracted position when the drive nut 566
is still coupled to the rack gear 90 as shown in FIG. 47, however,
the unfolded and retracted position equally applies to when the
drive nut 566 is initially coupled to the mirror bracket as shown
in FIG. 55. During a normal driving position, the unfolded and
retracted position is preferably defined with the drive nut 566
coupled to the mirror bracket 518 as shown in FIGS. 54 57 since the
coupling of the drive nut 566 to the mirror bracket 518 allows for
manual (or inadvertent) repositioning of the mirror housing with
respect to the base.
Returning to the description of the extension of the mirror
assembly 512 with reference to FIGS. 58 61, once the drive nut 566
is coupled to the mirror bracket 518 by the receipt of the pin 568
in the notch 542, the continued forward operation of the drive
screw 562 causes the drive nut 566 to traverse along the length of
the drive screw 562, which causes the mirror assembly 512 to also
move along with the drive nut 566 and move the mirror assembly 512
from the retracted position to the extended position shown in FIG.
58.
As best seen in FIG. 61, as the drive nut 566 traverses the drive
screw 562, the pin 568 rides in a channel 628 formed between the
upper edge of the C-shaped flange 530 and the outer edge of the
guide flange 614. As the drive screw 562 is operated in a forward
direction and rotates clockwise as viewed in FIG. 61, the drive nut
566 tries to rotate in the same direction causing the pin 568 to
bear against the upper flange of the C-shaped flange 530. When the
drive screw 562 is operated in a reverse direction and rotates
counterclockwise as viewed in FIG. 61, the drive nut 566 tries to
rotate in the same direction causing the pin 568 to bear against
the outer edge of the guide flange 614. Thus, the upper edge of the
C-shaped flange 530 limits the rotation of the drive nut 566 when
the mirror assembly is moved from the retracted to the extended
position, and the outer edge of the guide flange 614 limits the
rotation of the drive nut 566 when the mirror assembly is moved
from the extended to the retracted position.
FIG. 62 illustrates a simple control circuit suitable for
controlling the folding and extending functions of the mirror in
conjunction with the motor 564 and the limit switch 630. The
control circuit 632 preferably comprises a power extend switch 634
and a power fold switch 636, both of which are connected to the
limit switch 630 by switching diodes D1 and D2 to control both the
forward and reverse operation of the motor 564 and the range of
operation according to the selected fold and extend position of the
mirror. The limit switch works in combination with the power extend
and power fold switches 634, 636 to fold and extend the mirror
based on the selected position of the switches 634, 636 and the
position of the drive nut 566 as sensed by the state of the limit
switch 630. Preferably, the switches are configured to be mutually
exclusive so that a user cannot damage the control circuit (such as
by causing a short) by trying to perform a disallowed function,
e.g., by trying to fold and extend the mirror simultaneously. This
wiring feature is not shown for purposes of simplicity but such a
configuration would be apparent to one skilled in the art.
The limit switch 630 is preferably a single-pole double-throw micro
switch having pole 638 and contacts 640, 642. The power extend and
power fold switches are preferably double-pole double-throw
switches. The power extend switch 634 has poles 644, 642 and ground
contacts 648 and supply contacts 650. Similarly, the power fold
switch 636 has poles 656, 658 and ground contacts 660 and supply
contacts 662.
Switching diodes D1 and D2 connect the poles 640, 642 of the limit
switch 630 to the pole 644 of the power extend switch 634 and the
pole 656 of the power fold switch 636, respectively, and control
the direction of the current flow therebetween. The pole 638 of the
limit switch 630 connects to one side of the motor 564 and other
side of the motor 564 connects to the poles 646, 658 of the power
extend and power fold switches 634, 636, respectively, to complete
the coupling of the motor to the power extend and power fold
switches 634, 636 through the limit switch 630.
The power extend and power fold switches 634, 636 are both
three-position switches having an Up, Center, and Down position
when viewed in FIG. 62. For the power extend switch 634, the Up
position corresponds to extending the mirror assembly, the Center
corresponds to off, and the Down corresponds to the retracting the
mirror assembly. For the power fold switch 636, the Up position
corresponds to folding the mirror assembly, the Center corresponds
to off, and the Down corresponds to unfolding the mirror
assembly.
Depending on the selected positions of the power extend and power
fold switches 634, 636 in combination with the limit switch 630,
the control circuit 632 will effect the extension/retraction and
folding/unfolding of the mirror assembly to move the mirror
assembly into the position selected by the user.
FIG. 63 shows another embodiment of the control circuit 632 wherein
a microcontroller 664 replaces much of the hard-wired circuitry in
the previous embodiment. As can be seen in FIG. 63, the switches
(such as those shown by reference numerals 634, 636 and the limit
switch 630) are simply inputs to the microcontroller 664 and the
motor 564 is connected as an output thereof whereby the
microcontroller 664 can control the speed and direction of the
motor 564 through a suitable onboard program.
While it is preferred that the folding and extending functions of
the vehicle mirror 510 be accomplished by actuating the electric
motor 564 of the drive assembly 515 using a suitable control such
as that disclosed in FIG. 62, the vehicle mirror 510 has several
features that permit the manual folding and extension of the mirror
assembly 512. For example, the threads of the drive screw 562 have
a sufficiently long lead compared to the diameter of the drive
screw 562 to permit the manual extension and retraction of the
mirror assembly when suitable force is applied. The electric motor
564 preferably has a clutch that permits the release of the drive
screw 562 from the motor upon the application of the manual force,
thereby eliminating the tendency for the electric motor to prevent
the rotation of the drive screw 562.
Another feature useful for the manual operation of the mirror is
the detent assembly 570 which enables the mirror assembly 512 to be
rotated between the folded and unfolded positions in response to a
suitable manual force. The manual force must be great enough to
cause the dogs 584 on the spur gear 576 to ride up over the
projections 554 on the base 550.
FIGS. 64 87 illustrate a fifth embodiment of the vehicle mirror
assembly 510 having both a power-fold and a power-extend function.
The vehicle mirror assembly 510 comprises a mirror assembly 512 and
is mounted to a vehicle by a support bracket or arm 514. Referring
to FIG. 64, the mirror assembly 512 is connected to the support arm
514 by a drive assembly 665, which is used to rotate the mirror
assembly between folded and unfolded positions and extend the
mirror assembly between retracted and extended positions. In this
embodiment, the drive assembly 665 comprises components of three
modules: a basic component module 708 (see also FIG. 84), a
power-fold component module 710 (see also FIG. 86), and a
power-extend component module 712 (see also FIG. 85). It will be
understood that where the first embodiment illustrates all three
modules in the drive assembly 665, other embodiments may
incorporate less than all three modules or other modules, as
explained below.
Referring now to FIGS. 64 66, the mirror assembly 512 comprises a
mirror housing 516 in which is received a mirror bracket 518 that
supports a mirror drive 520 for adjusting the position of the
mirror 522 mounted to the mirror drive 520. The mirror drive 520
and mirror 522 are well known and will not be described in further
detail.
Referring specifically to FIGS. 66 and 68, the mirror bracket 518
comprises a generally planar upper face 528 on which the mirror
drive 520 is conventionally mounted. A C-shaped flange 530 extends
away from the planar face 528 and defines a forward-facing channel
532. A laterally extending plate 534 extends from the lower end of
the flange 530.
Referring specifically to FIG. 64, slots 536 are formed in the
lower wall of the flange 530. Tabs 538 extend from the lower edge
of the flange 530 and are adjacent the slots 536. A catch 540
extends laterally from the planar face 528 on the side opposite the
mirror drive 520 and has a U-shaped notch 542.
The support arm 514 comprises a shoulder 548 adapted to mount to
the vehicle and a base 700 extending laterally from the shoulder.
The base 700 has a generally flat upper surface 702 with an opening
704 having several notches 706 about its periphery.
The drive assembly 665 in the embodiment shown in FIG. 64 comprises
a basic component module 708, a power-fold component module 710,
and a power-extend component module 712. Looking now at FIGS. 64
and 81 84, the basic component module 708 comprises a main housing
714 in which is disposed an electric motor 716. A main gear 718 has
a spur portion 720 and a worm portion 722 and rotates on a spindle
in the main housing 714 in a position where the spur portion 720
engages a worm gear 723 on the shaft of electric motor 716. A
helical gear 724 has external teeth that mesh with the worm portion
722 of the main gear 718. The helical gear 724 is also hollow,
having a shaft 726 secured therein by a crimp 728 on its proximal
end. The shaft 726 has a spur gear 730 on its distal end that abuts
the helical gear 724. A spring 732 and a washer 734 between the
crimp 728 and the shaft 726, inside the helical gear 724, provide a
slip clutch that will enable the shaft 726 to rotate freely within
the helical gear 724 when torque on the shaft exceeds a
predetermined level, thus comprising a force-modifying device. An
upper cover 736 secures the aforementioned components within the
main housing 714.
Looking now at FIG. 85, the power-extend component module 712
comprises a drive screw 737 adapted to be coupled to the electric
motor 716 by an adapter 738 which clamps tabs 735 extending from
the drive screw to the shaft 726. It is within the scope of the
invention for the drive screw 737 to be secured to the shaft 726 in
any conventional manner. It is important only that the electric
motor 716 thus rotates the drive screw 737 about the longitudinal
axis of the drive screw 737. An internally threaded drive nut 739
is threadably received on the drive screw 737 and comprises a pin
741 extending laterally from the drive nut 739 along an axis that
is perpendicular to the longitudinal axis of the drive screw
737.
The power-fold and -extend component module 712 further comprises a
rack gear 740 and a guide bracket 742. The rack gear 740 comprises
a rail 744 having a series of teeth 746 on an inner surface
thereof. The rail 744 terminates in a tab 748 having a notch
750.
Referring now more closely to FIGS. 65 66, the guide bracket 742
comprises a main plate 754 from which extends a mounting tab 756
adapted to couple the guide bracket 742 to the main housing 714. A
limit flange 760 extends laterally from an upper end of the plate
754 and ends at a post 762, which transitions into a guide flange
764 having a slot 766 formed therein.
Looking now at FIGS. 64 and 81, a slightly V-shaped cam 768
comprising upper and lower fingers 770, 772 is mounted to the post
762 by a pin 774 received within the post 762. A cam surface 776 is
formed between the upper and lower fingers 770, 772. When the cam
768 is mounted to the post 762, the lower finger 772 is aligned
with the slot 766. A limit switch 780 can optionally be mounted to
the post 762 such that the switch 780 overlies the notch 542.
Referring to FIGS. 64 and 86, the power-fold component module 710
comprises an axle 810 having several longitudinal ribs 812 and a
flange 814 at one end. The axle 810 is secured in the opening 704
of the base 700 with the longitudinal ribs 812 received in the
notches 706. The flange 814 abuts a plate inside the main housing
714. A lower housing cover 816 is shaped to conform to a lower
portion of the main housing 714, and has a central opening 818
having a diameter large enough to encompass the ribs 812 of the
axle 810. Two bosses 820 extend upwardly from the lower housing
cover 816 and are disposed opposite each other adjacent the central
opening 818.
Surrounding the axle 810 between the flange 814 and the lower
housing cover 816 are a ring gear 822, an upper detent 824, a coil
spring 826, and a ramp 828. The internal diameter of the ring gear
822 is large enough to encompass the longitudinal ribs 812 of the
axle 810. The ring gear 822 bears against the flange 814. The side
of the ring gear 822 away from the flange 814 has a number of dogs
830 projecting therefrom. The upper detent 824 is a ring having an
internal diameter substantially the same as the outside diameter of
the axle 810 and a number of notches 832 corresponding to the
longitudinal ribs 812. The upper detent 824 is received over the
axle 810 and bears against the ring gear 822, so that the
longitudinal ribs 812 engage the notches 832 to prevent rotation of
the upper detent relative to the axle. The side of the upper detent
824 bearing against the ring gear 822 has detents 834 sized and
located to correspond to the dogs 830 projecting from the ring gear
822. Thus, when the upper detent 824 is pressed against the ring
gear 822, rotation of the ring gear 822 relative to the axle 810 is
inhibited by interengagement of the dogs 830 and the detents
834.
The coil spring 826 is disposed over the axle 810 between the upper
detent 824 and the ramp 828. The ramp 828 is a ring having an
internal diameter substantially the same as the outside diameter of
the axle 810, and, like the upper detent 824, has a number of
notches 836 corresponding to the longitudinal ribs 812. The
longitudinal ribs 812 engage the notches 836 to prevent rotation of
the ramp 828 relative to the axle 810. One side of the ramp 828
bears against the coil spring 826, and the other side bears against
the lower housing cover 816. The side of the ramp 828 facing the
lower housing cover 816 has two axial recesses 838 complementary in
shape to the bosses 820 extending upwardly from the lower housing
cover 816. However, the axial recesses 838 extend over a
predetermined radial angle, which in this embodiment is
approximately 90 degrees, defined by terminal ends of the axial
recesses 838. The preferred angle is the angle of motion desired
between the folded and unfolded positions, since the terminal ends
of the axial recesses will serve as stops for the bosses 820 on the
lower housing cover 816.
When all of these elements of the power-fold complement module 710
are assembled, the coil spring 826 is under compression so that on
the one hand, the upper detent 824 presses the ring gear 822
against the flange 814 and prevents rotation of the ring gear
relative to the axle 810. On the other hand, the ramp 828 is held
against the lower cover housing 816, but the lower cover housing
816 is permitted to rotate relative to the axle 810 within the
limits of the axial recesses 838.
The power-fold component module 710 also includes a traverse gear
840 for use when the power-fold component module 710 is assembled
without the power-extend complement module 712. In this
configuration, best illustrated in FIG. 86, the traverse gear 840
comprises a worm portion 842 and a spur portion 844. The helical
gear 724 is disposed 90 degrees from its earlier-described
position, with the external teeth of the helical gear 724 engaging
the worm portion 722 of the main gear 718. The traverse gear 840 is
positioned in the main housing 714 immediately beneath the helical
gear, with the worm portion 842 engaging the teeth of the ring gear
822, and the spur portion 844 engaging the teeth of the spur gear
730 on the shaft 726.
When the power-extend component module 712 is assembled to the
power-fold component module 710 in the drive assembly 665, the rack
gear 740 extends through a notch 846 in the main housing 714 (see
FIGS. 84 87) so that its teeth mesh with the teeth of the ring gear
822 and the rail 744 rests on the tab 756. It will be apparent that
actuation of the electric motor 716 will automatically urge the
mirror assembly 512 to extend or retract and fold or unfold as
described hereinafter.
For convenience, the operation of the vehicle mirror assembly 512
will be described beginning with the mirror assembly 512 in the
initially unfolded and retracted position as illustrated in FIGS.
66 68. In this position, the pin 741 of the drive nut 739 is
received within the notch 750 of the rack gear 740, and the drive
screw 737 has been rotated by the electric motor 716 a sufficient
amount that the drive nut 739 is positioned longitudinally along
the drive screw 737 such that the pin 741 lies beneath the cam
surface 776 formed by the upper and lower fingers 770, 772 and in
alignment with the slot 766. The lower finger 772 is rotated
exteriorly of the slot 766, and the upper finger 770 is received
within the notch 542 on the catch 540 of the mirror bracket 518.
The upper finger 770 is also spaced from the switch 780, leaving
the switch 780 in its naturally open state.
From the initial unfolded and retracted position as illustrated in
FIGS. 66 68, the reverse operation (counter-clockwise rotation of
the drive screw 737 as seen in FIG. 68) of the electric motor 716
will ultimately cause the mirror to rotate from the unfolded
position to the folded position as illustrated in FIGS. 69 72, and
the forward operation (clockwise rotation as seen in FIG. 68) of
the electric motor will initially transition the drive nut 739 from
coupling with the rack gear 740 to coupling with the mirror bracket
518 as illustrated in FIGS. 73 76 and ultimately cause the mirror
assembly 512 to extend from the retracted position to the extended
position as illustrated in FIGS. 77 80. The reverse operation of
the electric motor 716 results in the drive nut 739 moving towards
the electric motor 716 and the forward operation of the electric
motor 716 results in the drive nut 73 moving away from the electric
motor 716.
Referring to FIGS. 69 72, the movement of the mirror assembly 512
from the unfolded to the folded position will be described in
further detail. Upon the reverse operation of the electric motor
716, the drive nut 739, whose pin 741 is still received within the
notch 750, is drawn toward the electric motor 716, which, in turn,
urges the rack gear 740 toward the shoulder 548 of the support arm
514. If the ring gear 822 were free to rotate about the axle 810
and were not constrained by the upper detent 824, the urging of the
rack gear 740 toward the shoulder 548 would merely rotate the ring
gear 822 relative to the axle 810. However, since the ring gear 822
is held by the upper detent 824, the motion of the rack gear 740
causes it to traverse the exterior of the ring gear 822, causing
the rack gear 740 to rotate rearwardly carrying with it the main
housing 714 and, thus, the mirror bracket 518 to rotate the mirror
assembly 512 into the folded position.
Referring specifically to FIG. 72, when the drive screw 737 is
rotated to effect the longitudinal movement of the drive nut 739
relative to the drive screw 737, the pin 741 is retained within the
notch 750 by the limit flange 760. The limit flange 760 acting on
the pin 741 prevents the nut 739 from rotating with the drive screw
737 as it naturally would instead of traversing along the drive
screw 737 as desired. The combination of the notch 750 and the
limit flange 760 effectively limits or prevents the relative
rotation of the drive nut 739 to the drive screw 737, which causes
the drive nut 739 to traverse the drive screw 737 upon the rotation
of the drive screw 737.
To return the mirror assembly 512 from the folded position to the
unfolded position, the electric motor 716 is operated in the
opposite direction causing the rack gear 740 to once again traverse
the exterior of the ring gear 822 and rotate in a forward
direction, thereby rotating the mirror assembly 512 from the folded
to the unfolded position. The forward and reverse operation of the
electric motor 716 can therefore be used to cycle the mirror
assembly 512 between the folded and unfolded positions as
described. The limits of travel between the folded and unfolded
positions are determined by the radial angle of the axial recesses
838, which effectively stop rotation of the mirror assembly 512
when the bosses 820 on the lower housing cover 816 contact the end
of the axial recesses as the cover 816 rotates relative to the axle
810. Undue strain on the motor 716 is prevented when the stop is
hit by the slip clutch in the helical gear 724.
Referring to FIGS. 66 and 73 76, the transition of the drive nut
739 from coupling with the rack gear 740 to coupling with the
mirror bracket 518 for initiating the extension and retraction of
the mirror assembly 512 will be described in further detail. As
previously described, in the unfolded and retracted position as
illustrated in FIG. 66, the pin 741 of the drive nut 739 is
received within the notch 750 of the rack gear 740 to couple the
drive nut 739 to the rack gear 740. However, the further forward
operation of the drive screw 737 will not yield an extension of the
mirror assembly 512, since the drive nut 739 is not directly
coupled to the mirror bracket 518 or indirectly coupled to the
mirror bracket through another structural item such as the guide
bracket 742. Therefore, the drive nut 739 must be coupled to the
mirror bracket 518 to effect the movement of the mirror assembly
512 from the retracted position to the extended position.
The forward operation of the drive screw 737 accomplishes the
uncoupling of the drive nut 739 from the rack gear 740 and the
coupling of the drive nut 739 to the mirror bracket 518. When the
mirror assembly 512 is in the unfolded and retracted position
illustrated in FIG. 66, the pin 741 is aligned with the slot 766 in
the guide bracket 742. Since the pin 741 is no longer rotationally
constrained by the limit flange 760, the continued forward
operation of the drive screw 737 will result in the drive nut 739
rotating along with the drive screw 737 instead of longitudinally
traversing the drive screw 737 until the pin 741 is received within
the notch 542 of the catch 540 extending from the mirror bracket
518 to couple the drive nut 739 to the mirror bracket 518. As the
drive nut 739 rotates with the drive screw 737, the pin 741 follows
the cam surface 776 of the cam 768 causing the cam 768 to rotate,
resulting in the lower finger 772 entering the slot 766 and the
upper finger 770 moving out to the notch 542 and activating the
limit switch 780 to indicate that the drive assembly 665 is now
positioned for extension and retraction of the mirror assembly
512.
It should be noted that for convenience and to simplify the
description of the invention, the mirror assembly is described as
being in the unfolded and retracted position when the drive nut 739
is still coupled to the rack gear 740 as shown in FIG. 66, however,
the unfolded and retracted position equally applies to when the
drive nut 739 is initially coupled to the mirror bracket as shown
in FIG. 74. During a normal driving position, the unfolded and
retracted position is preferably defined with the drive nut 739
coupled to the mirror bracket 518 as shown in FIGS. 73 76 since the
coupling of the drive nut 739 to the mirror bracket 518 allows for
manual (or inadvertent) repositioning of the mirror housing with
respect to the base.
Returning to the description of the extension of the mirror
assembly 512 with reference to FIGS. 77 80, once the drive nut 739
is coupled to the mirror bracket 518 by the receipt of the pin 741
in the notch 542, the continued forward operation of the drive
screw 737 causes the drive nut 739 to traverse along the length of
the drive screw 737, which causes the mirror assembly 512 to also
move along with the drive nut 739 and move the mirror assembly 512
from the retracted position to the extended position shown in FIG.
77.
As best seen in FIG. 80, as the drive nut 739 traverses the drive
screw 737, the pin 741 rides in a channel 778 formed between the
upper edge of the C-shaped flange 530 and the outer edge of the
guide flange 764. As the drive screw 737 is operated in a forward
direction and rotates clockwise as viewed in FIG. 80, the drive nut
739 tries to rotate in the same direction causing the pin 741 to
bear against the upper flange of the C-shaped flange 530. When the
drive screw 737 is operated in a reverse direction and rotates
counterclockwise as viewed in FIG. 80, the drive nut 739 tries to
rotate in the same direction causing the pin 741 to bear against
the outer edge of the guide flange 764. Thus, the upper edge of the
C-shaped flange 530 limits the rotation of the drive nut 739 when
the mirror assembly 512 is moved from the retracted to the extended
position, and the outer edge of the guide flange 764 limits the
rotation of the drive nut 739 when the mirror assembly 512 is moved
from the extended to the retracted position.
As previously described herein with respect to the second
embodiment of the mirror assembly, FIG. 62 illustrates a simple
control circuit suitable for controlling the folding and extending
functions of the mirror, which can be utilized for the embodiment
of the mirror assembly described herein and which operates in the
same fashion. Similarly, the control circuit shown in FIG. 63 can
be used to control the folding and extending functions of the
mirror in a fashion similar to the embodiment previously
described.
FIG. 81 illustrates an embodiment of the power-fold component
module 710 as it would be installed in a vehicle mirror assembly
512. It will be noted that in this embodiment there is no
functionality for the power-extend function. FIG. 82 illustrates an
embodiment of the power-extend component module 712, as it would be
installed in a vehicle mirror assembly 512. It will be noted that
in this embodiment there is no functionality for the power-fold
function.
While it may be preferred to have either or both the power-fold and
power-extend functions in a vehicle mirror assembly 512, it will be
appreciated that the unique structure of the modular components
will permit manual folding and extension of the mirror assembly 512
notwithstanding the existence of the power functionality. The
threads of the drive screw 737 preferably have a sufficiently long
lead compared to the diameter of the drive screw 737 to permit the
manual extension and retraction of the mirror assembly 512 when
suitable force is applied. The slip clutch in the helical gear 724
permits the release of the drive screw 737 from the motor upon the
application of the manual force, thereby eliminating the tendency
for the electric motor to prevent the rotation of the drive screw
737. Moreover, application of manual force to fold the mirror
assembly 512 when the power-fold component module 710 is installed
can be accomplished by overcoming the force of the spring 826
holding the upper detent 824 in engagement with the ring gear 822.
When rotational force is applied to the ring gear 822, as when the
mirror assembly is manually urged to a folded position, the dogs
830 depending from the ring gear will be urged out of the detents
834 to depress the upper detent 824 against the force of the coil
spring 826, i.e. the detents and the dogs comprise a
force-modifying device. When the dogs 830 are freed from the
detents 834, the ring gear 822 is then free to rotate relative to
the axle 810, permitting manual rotation of the mirror assembly
512.
A manual component module 850 is illustrated in FIG. 83. It will be
apparent that the manual component module 850 comprises all of the
elements of the power-fold complement module 710 other than those
necessary for powered motion. In other words, the main housing 714,
upper housing cover 736, lower housing cover 816, axle 810, ring
gear 822, upper detent 824, coil spring 826, and ramp 828 are
included in the manual component module 850. The motor 716, main
gear 718, and traverse gear 840 are not included. Manual folding of
the mirror between the folded and unfolded positions is
accomplished by manually urging the mirror housing 512 toward the
folded position.
FIG. 84 shows the elements of the basic component module 708 which
are common to both the power-fold component module 710 and the
power-extend component module 712. FIG. 85 shows the elements of
the power-extend component module 712 and FIG. 86 shows the
elements of the power-fold component module 710. FIG. 87 shows the
elements of both the power-fold component module 710 and the
power-extend component module 712 combined as needed for a
power-fold and extend component module 860.
The modular arrangement of these elements benefits the assembly of
a vehicle mirror with preselected functionality. For example, the
different modules can be color coded so that when a particular
order appears on the assembly line for a mirror with a
predetermined functionality, the assembler can easily select the
components for a particular module. It is possible for the
predetermined components to be delivered to the assembler
automatically by a computerized system recognizing a color code or
other code associated with the selected module.
A sixth embodiment comprising a pivot mechanism for a mirror
assembly 910 is shown in FIGS. 88 98. The mirror assembly 910 is
similar in several respects to the mirror assemblies previously
described herein and comprises a frame 918, a reflective element
assembly 920, and a pivot assembly 922 which is mounted to a
vehicle (not shown) in a generally conventional manner. The mirror
assembly comprises a shell (not shown) which houses the reflective
element assembly 920, the pivot assembly 922, and, optionally,
other mirror components such as a power tilt assembly, turn
signals, and puddle lights.
Referring specifically to FIGS. 88 91, the frame 918 comprises an
irregularly-shaped body configured and adapted for the purposes
described herein, and comprising a pivot assembly housing 930 at a
first end and a reflective element mounting arm 932 at a second
end. The reflective element mounting arm 932 comprises a generally
conventional reflective element pivot mount 934 for pivotably
mounting the reflective element assembly 920 to the frame 918.
Intermediate the pivot assembly housing 930 and the reflective
element mounting arm 932 is a tilt actuator assembly housing 936
adapted for housing a tilt actuator assembly (not shown) for
selectively tilting the reflective element assembly 920 about a
horizontal and a vertical axis.
The pivot assembly housing 930 comprises a cylindrical wall 940
terminating in a first, upper rim 941 and a second, lower rim 943.
Intermediate the upper rim 941 and the lower rim 943 is an annular
floor 942 extending from the cylindrical wall 940 to an annular
wall 944 extending upwardly from the annular floor 942 toward the
upper rim 941 and defining a circular pivot bore 946. The
cylindrical wall 940 annular floor 942, and annular wall 944 define
an upper annular spring chamber 948. As shown in FIG. 90, the
cylindrical wall 940 and annular floor 942 define a lower gear
chamber 950, the gear chamber 950 being separated from the spring
chamber 948 by the annular floor 942. Extending from the lower rim
943 are a plurality of bosses 952 comprising a generally truncated
triangular-shaped body having a pair of juxtaposed inclined faces
954 terminating in a bottom face 956. In the preferred embodiment,
three bosses 952 are positioned around the lower rim 943 at an
interval of approximately 120.degree..
Referring now to FIG. 95, a pivot frame 960 is an
irregularly-shaped member comprising a mounting portion 962 and a
pivot base 964 in cantilevered juxtaposition to the mounting
portion 962. The mounting portion 962 is adapted for mounting the
vehicular mirror assembly 910 to the vehicle in a generally
conventional manner. The pivot base 964 cantilevers laterally from
the mounting portion 962 and comprises an annular floor 966 adapted
to be generally horizontal when the vehicular mirror assembly 910
is mounted to the vehicle. The annular floor 966 transitions to an
upwardly extending cylindrical wall 968 forming a collar 970
terminating in a rim 972. Extending upwardly from the annular floor
966 is a plurality of outer bosses 974. Extending upwardly from the
rim 972 is a plurality of inner bosses 976. The outer bosses 974
comprise generally truncated triangular-shaped bodies having a pair
of juxtaposed inclined faces 984. The inner bosses 976 comprise
generally truncated triangular-shaped bodies having a pair of
juxtaposed inclined faces 986. The outer bosses 974 are preferably
positioned about the annular floor 966 for mating communication
with the bosses 952 at an interval of approximately 120.degree. so
that the bosses 952 are brought into contact with the bosses 974
when the mirror assembly 910 reaches its fully extended position.
The inner bosses 976 are also preferably positioned about the rim
972 at an interval of approximately 120.degree.. The cylindrical
wall 968 terminates in an annular floor 982 extending from the
cylindrical wall 968 to a pivot post 978 extending upwardly from
the annular floor 982 and defining an annular space 980.
Referring now t0 FIGS. 91 and 92, a pivot gear 990 comprises an
annular body 992 having a plurality of circumferentially-spaced
gear teeth 994 and a pivot post aperture 996 coaxially extending
therethrough. The pivot post aperture 996 is adapted for slidable
receipt of the pivot gear 990 over the pivot post 978.
Referring to FIG. 98, the pivot gear 990 has a generally planar top
face 998 and a generally planar bottom face 1000 in parallel,
spaced-apart relationship. The bottom face 1000 is provided with a
plurality of radially extending detents 1001 comprising a pair of
juxtaposed inclined walls 1002 for mating communication with the
inner bosses 976.
In the preferred embodiment, the detents 1001 are positioned around
the bottom face 1000 at an interval of approximately 120.degree.. A
helical spring 1004 having a size and spring rate sufficient for
the purposes described herein is adapted for slidable insertion
over the annular wall 944 to occupy the spring chamber 948. A
generally conventional friction washer 1006 is adapted for
frictional insertion over the pivot post 978 to be frictionally
retained thereon.
Referring now to FIGS. 92 94, a drive assembly 1010 comprises a
helical gear, such as the worm 1012 shown in FIGS. 92 and 93, a
clutch gear 1020, an electric motor 1040, and a worm gear 1044. The
worm 1012 is a somewhat cylindrically-shaped elongated member
having a short shaft 1014, a long shaft 1016, and a gear portion
1018 in coaxial alignment. A clutch gear 1020 comprises an annular
flange 1022 having a planar collar face 1024 transitioning to an
annular collar 1026 extending coaxially from the annular flange
1022. The annular collar 1026 is provided with a plurality of
radially-extending collar slots 1028 extending through the annular
collar 1026 to divide the collar 1026 into arcuate collar fingers
1030. In the preferred embodiment, the slots are spaced at
90.degree. to form four equally spaced collar fingers 1030. The
annular collar 1026 defines a cylindrical shaft bore 1032 for
slidably receiving the long shaft 1016. The circumference of the
annular flange 1022 is provided with a plurality of gear teeth
1034. A clutch spring 1036 comprises a helical spring adapted for
frictional insertion over the annular collar 1026 to exert an
inwardly directed compressive force on the collar fingers 1030,
thereby comprising a force-modifying device.
The motor 1040 is a generally conventional 12-volt DC electric
motor having an axle 1042 extending therethrough fitted with a worm
gear 1044 for rotation as the motor 1044 is operated. The worm gear
1044 is adapted for operable communication with the clutch gear
1020. The worm 1012 is adapted for operable communication with the
pivot gear 990.
As assembled, the clutch spring 1036 urges the collar fingers 1030
into frictional communication with the long shaft 1016 so that the
rotation of the clutch gear 1020 will urge the worm 1012 into
rotation. However, if a resistance of a sufficient magnitude
prevents the rotation of the worm 1012, the clutch gear 1020 will
overcome the frictional resistance between the fingers 1030 and the
long shaft 1016 and the clutch gear 1020 will rotate. As shown in
FIG. 92, as the motor 1040 is operated, the rotation of the worm
gear 1044 will rotate the clutch gear 1020 which will, in turn,
rotate the worm 1012. Rotation of the worm 1012 will rotate the
pivot gear 990. The assemblage of the motor 1040 and the drive
assembly 1010 is fixedly retained in a suitable housing in the
frame 918.
As shown in FIG. 97, the pivot assembly 922 is assembled by placing
the pivot gear 990 over the pivot post 978 for slidable rotation of
the pivot gear 990 around the pivot post 978. The pivot gear 990 is
initially oriented so that the inner bosses 976 engage the detents
1001. The pivot assembly housing 930 is then assembled to the pivot
base 964 by inserting the pivot bore 946 over the pivot post 978 so
that the annular floor 942 engages the top face 998 of the pivot
gear 990. The pivot spring 1004 is then inserted over the pivot
post 978 in contact with the annular floor 942 and secured in place
by the friction washer 1006 inserted over the pivot post 978. As so
assembled, the spring 1004 will tend to urge the pivot assembly
housing 930 downwardly against the pivot gear 990, urging the pivot
gear 990 downwardly against the collar 970. In the preferred
embodiment, the bottom faces 956 of the bosses 952 will be spaced
away from the annular floor 966. In its normally operated
condition, the pivot gear 990 will remain fixed relative to the
pivot frame 960.
As shown in FIGS. 91 and 92, as discussed above, the worm 1012 is
in operable communication with the pivot gear 990 so that the worm
1012 will travel along the pivot gear 990 as the worm 1012 is
rotated. In the assemblage described herein, rotation of the worm
1012 will cause the drive assembly 1010 to traverse the perimeter
of the pivot gear 990, thus pivoting the frame 918 relative to the
pivot frame 960. When the inclined faces 954 of the bosses 952
contact the inclined faces 984 of the outer bosses 974, the frame
918 will stop relative to the pivot frame 960, corresponding to
either the fully extended or fully retracted position. If the motor
1040 continues to operate, the worm 1012 will be prevented from
rotating. However, the clutch gear 1020 will slip relative to the
worm 1012 and will continue to turn until the motor 1040 reaches a
shutoff condition.
In the event that the vehicular mirror assembly 910 is forced from
a fully extended position or a fully retracted position, such as by
an unintended impact, the pivot gear 990 will rotate relative to
the pivot frame 960 if the impact is sufficient to overcome the
interlocking of the inner bosses 976 and the detents 1001. The
bosses 952 will also be urged into moving relative to the outer
bosses 974. The detents 1001 will disengage from the inner bosses
976 by the inclined walls 1002 traveling upwardly and along the
inclined faces 986. At the same time, the frame 918 can rotate
relative to the pivot frame 960 by the inclined faces 954 traveling
upwardly and along the inclined faces 984 to translate the bosses
952 relative to the outer bosses 974. It will be obvious that this
movement must overcome the compression of the spring 1004 tending
to resist the upward movement of the pivot gear 990 and the frame
918. The compression of the spring 1004, and also the force needed
to move the mirror assembly 910, can be adjusted by the positioning
of the friction washer 1006 on the pivot post 978 to selectively
provide a greater or lesser compressive force.
If the vehicular mirror assembly 910 is forced from a fully
extended position or a fully retracted position as described above,
the pivot gear 990 will pivot so that the bottom face 1000
intermediate the detents 1001 is in supported communication with
the inner bosses 976, thereby "raising" the pivot gear 990 and the
frame 918 relative to the pivot base 964. The outer bosses 974 are
shorter than the inner bosses 976 so that, once the bottom face
1000 is supported on the inner bosses 976, the bosses 952 will
clear the outer bosses 974 and the frame 918 can further rotate
freely relative to the pivot base 964. The force of the spring 1004
will urge the bottom face 1000 against the inner bosses 976, and
the frictional force between the bottom face 1000 and the inner
bosses 976 will tend to resist movement between the bottom face
1000 and the inner bosses 976. In order to return the mirror
assembly 910 to its operable condition with the pivot gear 990
positioned so that the inner bosses 976 are again received in the
detents 1001, the mirror assembly 910 is activated by the driver of
the vehicle for retraction. This will cause the worm gear 1012 to
travel along the perimeter of the pivot gear 990, which will not
rotate due to the frictional force between the bottom face 1000 and
the inner bosses 976, and which will tend to pivot the frame 918
toward the fully retracted position. Once the frame 918 reaches the
fully retracted position, further rotation of the frame 918 will be
prevented, such as by a suitable assembly comprising mechanical
stops as is well-known in the industry. Consequently, the
frictional force between the bottom face 1000 and the inner bosses
976 will be exceeded, and the worm gear 1012 will begin to rotate
the pivot gear 990 until the inner bosses 976 are received in the
detents 1001, and the pivot gear 990 is returned to its normal
operating position on the pivot base 964 for extension and
retraction as previously described herein.
The novel pivot assembly provides a simplified clutch mechanism
comprising a minimum of elements for operating a power folding
mirror which provides protection against motor damage without
complex motor shutoff devices. The pivot assembly also provides a
simplified mechanism for accommodating unintended impact to the
mirror assembly tending to force the mirror from its fully extended
or fully retracted positions without damage to the pivot assembly
or the mirror.
FIGS. 99 104 illustrate a seventh embodiment comprising a pivot
connection for a mirror assembly having a circular array of
electrical contacts incorporated into the pivot connection. The
circular array of electrical contacts maintain electrical
conductivity for power and control signals between the vehicle's
power supply and control center and the various power functions
incorporated into the mirror irrespective of the pivotal
orientation of the mirror.
Referring also to FIGS. 99 and 103, the reflective element assembly
1120 comprises a reflective element or mirror 1116 mounted to a
glass case 1114, which is mounted in turn to a frame 1118
comprising a first portion having a reflective element mounting arm
1132 for mounting the reflective element 1116 and a second portion
having a pivot assembly housing 1130 comprising a portion of the
pivot assembly 1122.
As shown in FIG. 100, a single motor tilt actuator assembly 1128 is
mounted to the frame 1118. The reflective element 1116 is mounted
to the tilt actuator assembly 1128 for selectively tilting the
reflective element 1116 about a horizontal axis and a vertical axis
upon operation of the tilt actuator assembly 1128. Examples of a
single motor actuator assembly are disclosed in U.S. Patent
Applications No. 60/319,411 entitled "Single Motor Actuator With
Selectable Multiple-Output Axes And Vehicle Mirror Incorporating
Same," filed Jul. 19, 2002; 60/319,176 entitled "Single Motor
Actuator With Selectable Multiple Output Axle And Vehicle Mirror
Incorporating Same," filed Apr. 9, 2002; and 60/319,637 entitled
"Electric Motor With Selective Dual Shaft Output," filed Oct. 21,
2002, all of which are incorporated herein by reference.
Referring also to FIG. 101, the pivot assembly housing 1130
comprises an annular wall 1134 defining a pivot chamber 1136.
Spaced about the lower edge of the annular wall 1134 at regular
intervals, preferably intervals of 120.degree., are recesses 1138.
Electrodes, such as electrical leads 1150, 1152, 1154, comprise
electrically-conductive conduits, such as copper wire or straps,
and extend along the annular wall 1134 in radially-spaced
juxtaposition and through the frame 1118 for operable communication
with the tilt actuator assembly 1128. As shown in FIG. 101, the
outer lead 1150 extends adjacent the outer periphery of the annular
wall 1134 to terminate in a downwardly-depending outer contact
1156. The intermediate lead 1152 extends along the center of the
annular wall 1134 to terminate in a downwardly-depending
intermediate contact 1158. The inner lead 1154 extends adjacent the
inner periphery of the annular wall 1134 to terminate in a
downwardly-depending inner contact 1160. The contacts 1156, 1158,
1160 are in corresponding communication with the recesses 1138, and
thus are spaced at regular intervals along the annular wall 1134,
preferably intervals of 120.degree.. As shown in FIG. 101, the
contacts 1156, 1158, 1160 extend through the bottom of the annular
wall 1134 to form regularly-spaced electrical contact points along
the bottom of the annular wall 1134. The leads 1150, 1152, 1154 are
adapted to carry electrical power and control signals to the tilt
actuator assembly 1128 from the power supply and onboard controls
in the vehicle (not shown).
Referring also to FIG. 102, the base 1124 comprises a pivot portion
1140 comprising an annular floor 1142 and an annular wall 1146
extending upwardly therefrom for slidable insertion in the pivot
chamber 1136 and pivotal movement of the frame 1118 relative to the
base 1124. Spaced circumferentially about the annular wall 1146 for
cooperative communication with the recesses 1138 are
upwardly-extending bosses 1144. Electrodes, such as electrical
feeds 1170, 1172, 1174, comprise electrically-conductive conduits,
such as copper wire or straps, and extend in radially-spaced
arcuate paths along the annular floor 1142 for operable
communication with the contacts 1156, 1158, 1160, respectively. The
outer feed 1170 is adapted for electrical contact with the outer
contact 1156. The intermediate feed 1172 is adapted for electrical
contact with the intermediate contact 1158. The inner feed 1174 is
adapted for electrical contact with the inner contact 1160. As
shown in FIG. 102, the electrical feeds 1170, 1172, 1174 extend
onto the bosses 1144.
Referring again to FIG. 100, when the frame 1118 is assembled to
the base 1124 so that the annular wall 1140 is received in the
pivot chamber 1136, the outer contact 1156 will be in electrical
communication with the outer feed 1170, the intermediate contact
1158 will be in electrical communication with the intermediate feed
1172, and the inner contact 1160 will be in electrical
communication with the inner feed 1174. As the frame 1118 pivots
relative to the base 1124, the contacts 1156, 1158, 1160 will
travel along the feeds 1170, 1172, 1174, respectively, maintaining
electrical communication of the tilt actuator assembly 1128 with
the power supply and onboard controls in the vehicle. When the
reflective element assembly 1120 is folded completely against the
vehicle, the bosses 1144 will be displaced relative to the recesses
1138, thereby breaking the communication between the contacts 1156,
1158, 1160 and the feeds 1170, 1172, 1174. However, with the
reflective element assembly 1120 folded against the vehicle,
electrical communication of the tilt actuator assembly 1128 with
the power supply and onboard controls in the vehicle will be
unnecessary.
The leads 1150, 1152, 1154 can be integrated into the base 1124,
the annular floor 1142, and the bosses 1144, and the feeds 1170,
1172, 1174 can be integrated into the frame 1118, the annular wall
1134, and the recesses 1138 through a suitable method of forming
electrical circuits on or in a substrate, such as sputtering the
material onto the substrate, or embedding the leads and feeds into
the substrate.
A second embodiment of the electrical routing assembly shown in
FIGS. 99 102 is shown in FIGS. 103 104. FIG. 103 is a perspective
view showing the reflective element mounting arm 1132 in phantom
and having an external housing removed both for purposes of clarity
to show features of this embodiment relating to the provision of a
routing system for a heater element (referred to herein with
reference numeral 1180) through a mirror pivot mount 1178 on the
mounting arm 1132.
The heater element 1180 can comprise any suitable heater, typically
used for defrosting and other heating functions performed on the
reflective element 1116. In this case, a generally planar heating
pad is shown having a pair of conductive terminals 1182 thereon is
shown as an exemplary structure suitable for the heater element
1180. It will be understood that any known heater element for a
mirror can be employed herein without departing from the scope of
this invention.
With reference to FIGS. 103 104, the pivot mount 1178 on the
mounting arm 1132 is preferably gimbaled to a juxtaposted socket
1184 on the reflective element 1116. In addition, distal ends 1186
of actuators 1188 are interconnected in a known manner to the motor
1192 on the tilt actuator assembly 1128 are suitably mounted within
juxtaposed recesses 1190 on the reflective element 1116, preferably
on a backside thereof.
One feature of this embodiment is the provision of first and second
jumper leads 1194 and 1196 located on the mounting arm 1132 and the
reflective element 1116, respectively. The first jumper leads 1194
comprise elongated conductive members having a first end 1198
connected to at least one of the leads 1150 1154 and can be
interconnected via the motor 1192. The first jumper leads 1194 also
have a second end 12100 formed to the periphery of the pivot mount
1178 of the mounting arm 1132. As can be seen in FIGS. 103 104, the
second end 1200 of the first jumper leads 1194 extend along a stem
portion of the pivot mount 1178 and around a facial portion
thereof.
The second jumper leads 1196 comprise elongated conductive members
having a first end 1202 formed for connection the terminals 1182 on
the heater element 1180. The second jumper leads 1196 also have a
second end 1204 formed to the interior periphery of the socket 1184
of the reflective element 1116. As can be seen in FIGS. 103 104,
the second end 1204 of the second jumper leads 1196 extend into the
interior portion of the socket 1184 preferably in juxtaposition
with the first jumper leads 1194 located on the pivot mount 1178 of
the mounting arm 1132.
In assembly, the second embodiment of FIGS. 103 104 can be
employed, according to the invention, to interconnect the heater
element 1180 with the electrical circuit embedded in the mirror
assembly formed by the leads and contacts 1150 1160 as described
with respect to FIGS. 99 102. Each of the first and second jumper
leads 1194 and 1196 can comprise any suitable conductive structure,
such as the exemplary pair of parallel, conductive tracks shown in
FIGS. 103 104.
The first end 1198 of the first jumper leads 1194 are electrically
interconnected to one or more of the suitable leads and contacts
1150 1160 described with respect to FIGS. 99 102. The electrical
connections to the motor 1192 can be employed, especially with
respect to a common lead, as would be apparent to one skilled in
the art. The second end 1200 of the first jumper leads 1194 are
mounted as described above with the second end 1200 formed around
the pivot mount 1178 of the mounting arm 1132.
The first end 1202 of the second jumper leads 1196 are electrically
interconnected with the terminals 1182 on the heater element 1180
in a known manner. The second end 1204 of the second jumper leads
1196 are mounted as described above with the second end 1204
embedded into and extending into the interior periphery of the
socket 1184 on the reflective element 1116. As can be seen in FIG.
104, the second end 1200 of the first jumper leads 1194 make an
electrical connection with the second end 1204 of the second jumper
leads 1196 when the pivot mount 1178 of the mounting arm 1132 is
gimbaled within the socket 1184 on the reflective element 1116.
As will be appreciated by one skilled in the art, the leads 1194
and 1196, especially the second ends 1200 and 1204 thereof, are
preferably sized and mounted to their corresponding pivot mount
1178 and socket 1184 so that no short circuiting can occur between
the first and second jumper leads 1194 and 1196. As can be
appreciated, as the reflective element 1116 is pivoted with respect
to the mounting arm 1132 (such as through the action of the
actuators 1188 of the tilt actuator assembly 1128), the position of
the second end 1200 of the first mounting leads 1194 can angularly
adjust with respect to the second end 1204 of the second mounting
leads 1196. However, due to the juxtaposed relationship of the
second ends 1200 and 1204 of the first and second jumper leads 1194
and 1196 as well as the gimbal mounting of the pivot mount 1178
within the socket 1184, an electrical connection is maintained
between the first and second leads 1194 and 1196, respectively,
without regard to the particular angular or gimbal movement of the
reflective element 1116 with respect to the mounting arm 1132.
In this manner, the heater element 1180 can be electrically
interconnected to the leads and contacts 1150 1160 without
requiring a separate wiring routing and/or harness for such
interconnection. It will also be understood that, although an
interconnection between the heater element 1180 and the electrical
routing system is shown as a pair of jumper leads interconnected
through the gimbal connection at the pivot mount of 1178, the
jumpers can also simply be conventional jumper wires/leads
interconnecting the heater element 1180 (onboard with the
reflective element 1116) with the electrical routing assembly
onboard with the mounting arm and associated other portions of the
mirror assembly without departing from the scope of this
invention.
Another feature of the mirror assembly is also shown in FIGS. 103
104 in that a modified version of the leads and contacts 1150 1160
are shown. Specifically, the leads 1150 1154 are shown having a
raised portion which extends above the bosses 1144 on the annular
floor 1142 of the pivot portion 1140. In this manner, the
electrical connection is maintained between the leads 1150 1154 and
contacts 1156 1160 regardless of whether the pivot portion 1140 is
placed into an overtravel condition through contact or other manual
manipulation. That is, contrary to the previous embodiment of FIGS.
99 102, the mirror assembly maintains its electrical communication
throughout the system during a normal range of travel of the pivot
portion 1140 and any overtravel portions since the raised nature of
the leads 1150 1154 maintain contact with the contacts 1156 1160
throughout all ranges of travel.
The electrical routing assembly described herein provides
electrical communication between two pivoting parts without the
complicated wiring and equipment failure experienced with
conventional wire harnesses. The assembly of the electrical system
is simplified and all electrical hookups are made upon assembling
the reflective element assembly to the base, thereby eliminating a
separate wiring step in the manufacturing process. All necessary
electrical communication can be provided through a set of contacts
which travel along mating electrodes.
Referring now to FIG. 105, an eighth embodiment of a vehicular
mirror assembly 1210 is shown comprising a housing 1212, a base
1214 and a power assist device 1216. The base 1214 includes
mounting components (shown generally by reference numeral 1218) for
attaching the base to an exterior portion of a vehicle.
The power assist device 1216, while shown by example as a device
for pivotally moving the housing 1212 with respect to the base
1214, can be any motor-driven device including, but not limited to,
a mirror adjustment motor, a linear mirror housing extender, and
the like. Examples of these power assist devices 1216 can be found
in U.S. Pat. Nos. 6,206,553, 6,276,808 and 6,213,609, issued,
respectively, on Mar. 27, 2001, Aug. 21, 2001, and Apr. 10, 2001,
each of which is respectively incorporated herein by reference and
not further described herein.
With reference to FIGS. 105 106, the power-assist device 1216
includes a motor shut-off circuit 1220 which has first and second
leads 1222 and 1224 preferably interconnected to a motor 1232 of
the power-assist device 1216 and third and fourth leads 1226 and
1228 preferably interconnected to an on-board controller (not
shown) via a connector 1230. The shut-off circuit 1220 comprises a
delay timer 1234, a relay circuit 1236 and a current-sensing
circuit 1238 interconnected between the third and fourth leads
1226, 1228, and a motor 1232 via the first and second leads 1222,
1224. The delay timer 1234 preferably prevents premature switching
due to an inrush of current to the motor upon the startup of the
motor 1232. The relay circuit 1236 and the current-sensing circuit
1238 operate as a latching mechanism which preferably resets at the
instant supply power via the third and fourth leads 1226, 1228 is
removed, thereby allowing the motor 1232 to be used again without
delay.
The delay timer 1234, the relay circuit 1236 and the current
sensing circuit 1238 incorporated within the motor shut-off circuit
1220 will now be described with respect to FIGS. 107 111 in greater
detail. It will be understood that, the specific circuitry making
up the motor shut-off circuit 1220 is shown by example as one
appropriate configuration for accomplishing the structure and
functions outlined herein, but shall not be construed as limiting
on the scope of this invention. Rather, other circuitry components
could be substituted for those shown in FIGS. 107 111 without
departing from the scope of the invention. It will also be
understood that particular characteristics of the circuitry
components shown in FIGS. 107 111 are by example only, such as
resistance and capacitance values, and such values should not be
construed as limiting on the scope of the invention.
With respect to the circuit diagrams shown in FIGS. 107 111, it can
be seen upon an examination of these figures that the motor
shut-off circuit shown in the example of FIGS. 107 111 is made up
of capacitors, diodes, resistors, and relays. In order to ensure
consistency and clarity in the description provided herein as well
as to comport with typical electrical/circuit diagram conventions
the first character making up each identifier of a circuitry
component is identified with a letter corresponding to the
particular type of component followed by a unique numerical
identifier. For example, reference numerals for capacitors begin
with a "C" (e.g., C1, C2, . . . ), diodes begin with a "D" (e.g.,
D1, D2, . . . ), resistors begin with a "R" (e.g., R1, R2, . . . ),
transistors begin with a "Q" (e.g., Q1, Q2, . . . ), and relays
begin with a "U" (e.g., U1, U2, . . . ). Various nodes on the
shut-off circuit 1220 have reference numerals which begin with an
"N" (e.g., N1, N2. . . . ).
Turning to the example configuration of the motor shut-off circuit
1220 shown in FIG. 107, nodes N1 through N11 are shown on the
circuit diagrams. The third and fourth leads 1226, 1228
(respectively identified with typical wire identifiers RED and
BLACK) are connected to separate nodes N1 and N2, respectively.
Resistor R13 is located between nodes N1 and N3. Capacitor C9 is
located between nodes N3 and N2. Resistor R12 is located between
nodes N3 and N4. Node N4 terminates into base emitter junction of
transistor Q6. Transistor Q6 and diode D6 are wired in parallel
with transistor Q5 and diode D5 between nodes N5 and N2. Resistor
R4 is located between nodes N5 and N6 which, in turn, terminates in
a base emitter junction of transistor Q1. Transistor Q1, diode D2
and transistor Q4 are provided in parallel with transistor Q2,
diode D1 and transistor Q3 between nodes N7 and N11. Resistor R14
is located between nodes N11 and N2.
Node N7 terminates into a port labeled "A" of relay U8. A port "B"
of relay U8 is connected to node N1. The motor 1232 is connected
between nodes N1 and N9. Node N9 is also connected to a
normally-closed contacts NC of relay U8. Resistor R5 is connected
between node N9 and node N10. Node N10 terminates in base emitter
junction of transistor Q3. Resistor R2 is connected between nodes
N2 and N8. Node N8 terminates in a control port COM for relay U8
that, in turn, is connected by a loop to normally-open contacts NO
of relay U8.
As can be seen from the circuit diagrams of FIGS. 107 111, certain
of the circuit components are provided in opposing configurations
so that the motor 1232 of the shut-off circuit 1220 can be operated
bi-directionally, i.e., with differing polarities applied to the
third and fourth leads 1226, 1228. For example parallel
configurations of components D6-Q6 and D5-Q5 are provided in
opposing configurations. Parallel configurations of Q1-D2-Q4 and
Q2-D1-Q5 are also provided in an opposing arrangement.
The timer circuit 1234, the relay circuit 1236, and the current
sensing circuit 1238 of the motor shut-off circuit 1220 preferably
have the boundaries indicated by the dashed lines with like
reference numerals in the figures.
The operation of the motor shut-off circuit 1220 can generally be
described with respect to four states of operation. A first state
(see FIG. 108) is when power is initially applied to the shut-off
circuit 1220 via leads 1226, 1228. A second state (see FIG. 109) is
when the motor 1232 is running in a predetermined direction based
on the polarity of the power applied to leads 1226, 1228. A third
state (see FIG. 110) is when the motor 1232 has stopped, at an
instant in time immediately prior to triggering of the shut-off
circuit 1220. A fourth state (see FIG. 111) is when the motor 1232
has been switched off. Annotations of the proposed current paths
inherent in each state are shown on the state diagrams of FIGS. 107
111 and are labeled as currents I.sub.1, I.sub.2, . . . .
The first state is described with respect to FIG. 108. When power
is first applied to the leads 1226, 1228, capacitor C9 is
discharged and the voltage thereacross is below the forward voltage
drop of the base-emitter junction of Q6. Current I1 is therefore
charging C9 and Q6 is in an off position. In this first state, the
motor 1232 has not yet reached full operating speed and is drawing
a large inrush current 12. The voltage drop across R2 exceeds the
forward voltage drop of the base-emitter junction of Q3, so base
current 13 also flows through Q3. Since Q6 is switched off, Q2 is
also switched off and there is no current flow through the relay
coil. The relay contacts are normally closed, so current flows
through the contacts, and through R2, as long as the relay U8 is
not energized.
The second state is described with respect to FIG. 109. After
several milliseconds, C9 has sufficient charge to overcome the
forward voltage drop of the base-emitter junction of Q6. A current
I1 flows through the base of Q6, turning it on and thus allowing
current flow I3 through R4 and Q2. Resistor R4 limits current I3 so
that it is insufficient to energize the relay. By this time, the
motor 1232 has reached full operating speed and the motor current
I2 has dropped to a lower level. The resulting voltage drop across
R2 is now insufficient to turn on Q3, and the relay U8 remains
de-energized.
The third state is described with respect to FIG. 110. As in State
2, C9 is charged, i.e., the time delay has expired. Current I1
flows through Q6, turning it on and allowing current flow through
R4 and Q2, turning on Q2. The motor 1232 has either stalled or met
sufficient resistance to its travel so motor current I4 has
increased past the "switch-off" threshold. There is now sufficient
voltage drop across R2 to cause base current I5 to flow through Q3,
turning it on. Since Q2 is also turned on, due to the expiration of
the time delay, a current I3 flows which is sufficient to energize
the relay U8. This state depicts the instant before the contacts in
the relay actually move.
The fourth state is described with respect to FIG. 111. As in the
second and third states, currents I1 and 12 flow because the time
delay has expired. The relay U8 is now energized and the contacts
have opened, preventing current from flowing through R2. There is
still a small current I4 flowing through the motor 1232. Current
I4, because it is limited by R5 and R14, is insufficient to cause
the motor 1232 to turn or cause significant heating of the motor
winding, but it is sufficient to keep Q3 switched on and therefore
current I3 continues to flow. This keeps the relay U8 energized and
the circuit 1220 remains in this switched-off state until the
supply power is removed.
The following is a general description of the operational features
and benefits of the shut-off circuit 1220 for the motor 1232.
The shut-off circuit 1220 is preferably designed to turn on the
relay U8 when the current through the motor 1232, and therefore
resistor R2, reaches a preset amount. The motor 1232, however,
draws an initial surge of current while starting, and it can be
undesirable to have the shut-off circuit 1220 prematurely switch
off as a result of this initial current surge. Therefore, the
shut-off circuit 1220 also incorporates a time delay, which
disables the sensitivity of the shut-off circuit 1220 for a
predetermined period of time, such as several milliseconds (e.g.,
100 ms) after the initial application of the supply voltage.
Because it is desired to operate the motor in more than one
direction, the shut-off circuit 1220 is energized with an input
voltage via the leads 1226, 1228 of either a positive or negative
polarity. Since the circuit 1220 employs transistors which are
typically designed to operate at a single polarity, the shut-off
circuit 1220 incorporates a pair of transistors Q5, Q6 for each
function, one of type NPN and one of type PNP. When one transistor
Q5/Q6 of each pair is biased with the proper polarity, the other is
protected by a diode D5/D6, which keeps it switched off.
FIGS. 107 111 show the case where the lead 1226 (RED) is positive
and the lead 1228 (BLACK) is negative whereby diodes D2 and D5 are
reverse biased, preventing transistors Q1, Q4, and Q5 from
conducting. In this case, transistors Q2, Q3, and Q6 carry out the
function of the shut-off circuit 1220. Of course, the converse is
true when the polarity is reversed between the leads 1226,
1228.
The normally closed contacts NC of the relay U8 are wired in series
with the motor 1232. This allows the motor 1232 to run as long as
the relay U8 is not energized, i.e., the energizing current in the
relay coil is insufficient to switch the relay U8. Also in series
with the motor 1232 is a parallel circuit consisting of R2 on one
branch and the series combination of R5, R14, and the base-emitter
circuit of Q3 on another branch. Since the resistance of the R2
branch is relatively low, a majority of the current through the
motor 1232 is also conducted by R2.
As the load on the motor 1232 increases, the current through the
motor 1232 (and, therefore, R2) also increases. This produces a
voltage drop across R2 which is nearly proportional to the motor
1232 current. When the voltage across R2 reaches a sufficient level
to overcome the forward voltage of the base-emitter junction of Q3,
current flows through R5, R14, and the base of Q3, switching Q3
on.
If Q2 and Q3 provide sufficient current to energize the relay U8,
the normally closed contacts NC of the relay U8 open the R2 branch
of the circuit, leaving the motor 1232 in series with R5, R14, and
the base-emitter circuit of Q3. The resistance of the resulting
series circuit is too high for the motor 1232 to run, so the motor
1232 is effectively shut off. However, there is preferably still a
sufficient amount of current flow through the motor and the
remaining branch to keep Q3 switched on and the relay energized,
thereby latching the circuit 1220 in a shut-off state. The circuit
remains in this state until power is removed.
The shut-off circuit 1220, as mentioned earlier, is prevented from
shutting off within the first several milliseconds of the time
power is applied. This is accomplished through the use of the timer
circuit 1234, preferably an RC circuit in the figures composed of
R13 and C9. At the instant power is applied to the shut-off circuit
1220 via the leads 1226,1 1228, C9 is discharged and R13 drops the
full supply voltage. Therefore, at this same instant, Q6 is shut
off and, since there is no base current at Q2, it is also shut off.
This prevents the relay from energizing, even if Q3 is switched on
due to initial motor startup current.
As the voltage across C9 increases over time, it eventually reaches
a level sufficient to turn on Q6 through R12, which provides
current through its collector and R4 to turn on Q2. By this time,
the initial current spike drawn by the motor upon starting subsides
to the point where Q3 does not conduct enough current to energize
the relay U8. This state continues until the mechanism driven by
the motor 1232 reaches the end of its travel, or encounters an
obstruction, the point at which the motor current will again
increase enough to turn on Q3 and finally energize the relay U8 as
described previously, shutting off the motor 1232.
The operation of the shut-off circuit 1220 in the opposite polarity
(with respect to the leads 1226, 1228) is very similar, with Q1
serving the same function as Q2, Q4 as Q3, and Q5 as Q6,
respectively. In this case D1 and D6 are reverse biased, preventing
Q2, Q3, and Q6 from conducting.
Referring now to FIGS. 114 115, a schematic drawing of a driver
seated in a vehicle is shown, wherein a vehicle has a ninth
embodiment of a rearview mirror assembly movable between a
retracted and an extended position. It will be understood that,
with respect to elements of the schematic drawings shown in the
prior art version of FIGS. 112 113 and the inventive embodiment
shown in FIGS. 114 115, elements common to both sets of drawings
are identified with the same reference numerals.
A vehicle 1310 is shown having a rearview mirror assembly 1330
mounted thereto, wherein the rearview mirror assembly 1330
comprises a base 1332 mounted to the vehicle 1310 with a mirror
1334 mounted thereto for movement between a retracted position as
shown in FIG. 114 and an extended position as shown in FIG. 115. A
driver 1318 is shown seated within the vehicle 1310 and observing
an image shown in the mirror 1334 through a first field of view
1320 defined between the eyes of the driver 1318 and the mirror
1334. The image captured by the mirror 1334 is defined by a second
field of view 1324, shown in FIGS. 114 115, as capturing a
generally rearward direction adjacent to the vehicle 1310 as is
typically observed by drivers of vehicles.
The retractable and extendable movement of the mirror 1334 relative
to the base 1332 is accomplished by an adjuster 1336 whose function
is to reorient the mirror 1334 with respect to the base 1332. As
seen in FIGS. 114 115, the adjuster 1336 comprises a first arcuate
arm 1338 mounted to the base 1332 and a second arcuate arm 1340
mounted to the mirror 1334, wherein the second arcuate arm 1340 is
telescopingly received by the first arcuate arm 1338 for movement
between a retracted position as shown in FIG. 114 and an extended
position as shown in FIG. 115. As can be seen from FIGS. 114 115,
each of the first and second arcuate arms 1338, 1340 preferably has
an arcuate configuration. In this embodiment, the reorientation of
the mirror 1334 relative to the driver 1318 during the movement of
the mirror between the retracted and extended positions is
accomplished by the arcuate configuration of the adjuster 1336 and,
particularly, the arcuate configuration of the first and second
arcuate arms 1338, 1340.
Whereas in the prior art drawings shown in FIGS. 112 113, a linear
extension of the mirror relative to the base can undesirably
reposition (or, i.e., fail to reposition) the mirror so that an
undesirable blind spot condition is created, the inventive
configuration shown in FIGS. 114 115 automatically repositions the
mirror 1334 relative to the base 1332 by extending and/or
retracting the mirror 1334 relative to the base 1332 along an
arcuate path. It will be understood that this invention is equally
applicable to a manually-extendable mirror assembly as well as a
powered-extend mechanism wherein a motor extends and retracts the
mirror 1334 with respect to the base 1332.
FIGS. 116 121 show an embodiment of the mirror 1330 which includes
a housing 1342 enclosing the mirror 1334. FIGS. 116, 118 and 119
show the mirror assembly in a retracted position while FIGS. 117,
120 and 121 show the mirror assembly 1330 in an extended position.
As best shown in FIGS. 119 and 121, a first end 1344 of the first
arm 1338 is mounted to the base 1332, such as for pivotal movement
with respect to the base 1332 if the mirror assembly 1330 is
foldably mounted to the vehicle 1310 as is known in the art. A
second end 1346 of the first arm 1338 is telescopingly mounted to
the second arm 1340. Preferably, each arm 1338, 1340 has an arcuate
configuration such as that which can be seen in the drawings. The
second arm 1340 preferably has a mounting flange 1348 which
supports a mounting plate 1350.
The mounting plate 1350, on an outboard surface of thereof, has a
gimbal 1352 thereon which receives a socket 1354 on a rear surface
of the mirror 1334 for pivotally mounting the mirror 1334 to the
second arm 1346 in a "universal joint" fashion. The mirror assembly
1330 can also be provided with one or more automatic mirror
actuators (not shown) for positioning the mirror relative to the
housing 1342 as is known in the art, such as by actuation of a
switch located within a passenger compartment of the vehicle 1310
to adjust the view plane of the mirror 1334. As is known, the
mounting plate 1350 can include a "power pack", a motor and or
conventional actuators as would be apparent to one skilled in the
mirror-positioning art. Alternatively, the mirror 1334 can be
adjusted by manually positioning the mirror relative to the housing
1342 by digitary force imparted to one or more of the edges of the
mirror 1334 to pivot the mirror 1334 about the gimbal 1352.
The use of the embodiment of FIGS. 116 121 is relatively
straightforward. When the mirror assembly 1330 is in the retracted
position as shown in FIGS. 116, 118 and 119, the second arm 1340 is
received by the first arm 1338. When the mirror assembly 1330 is to
be moved to the extended position as shown in FIGS. 117, 120 and
121 such as by grasping the mirror housing 1342 and pulling
outwardly or by an on-board actuator motor (not shown), the second
arm 1340 is extended from the first arm 1338 because the second arm
1340 is attached to the mirror housing 1342 and the first arm 1338
is attached to the base 1332. As the mirror housing 1342 is moved
to the extended position, the mirror housing 1342 and, in turn, the
mirror 1334, moves along an arcuate path as defined by the first
and second arms 1338, 1340, respectively. This movement does not
change the position of the mirror 1334 with respect to the mounting
plate 1350 and the positioning of the gimbal 1352 with respect to
the mirror 1334 is unaffected as those are positions selected by
the driver 1318. The mirror assembly 1330 can be returned to the
retracted position by movement in the opposite direction.
While the embodiment shown in FIGS. 116 121 is suited for either
manual or powered movement of the mirror 1334 between the retracted
and extended positions, an additional embodiment of the mirror
assembly 1330 according to the invention is shown in FIGS. 122 125,
which further illustrates the concept of the addition of a
powered-extend function to the mirror assembly 1330. It will be
understood that reference numerals in FIGS. 122 125 have been
increased by 100 for components common to the previous embodiments
shown in FIGS. 114 121 and that these common components and/or
elements need not be re-described.
FIGS. 122 123 and 124 11254 show the mirror assembly 1430 in a
retracted and an extended position, respectively, in which a motor
1460 is mounted within the interior of the first arm 1438. The
motor 1460 has an output shaft 1462 which is interconnected to a
worm 1464. It will be understood that the motor 1460 and worm 1464
are preferably selected so that the length and volume occupied by
these components do not interfere with the extension and retraction
of the second arm 1440 with respect to the first arm 1438. Whereas
in the previous embodiments of FIGS. 114 121 the movement of the
mirror 1334 relative to the base 1332 was accomplished generally by
manual movement of the mirror 1334 and/or the housing 1342 relative
to the base 32, in this embodiment, the motor 1460 imparts motion
to the adjuster 1436 via the first and second arms 1438, 1440.
A travel nut 1466 is threadingly mounted to the worm 1464 in a
conventional manner. The nut 1466 comprises a conventional nut,
however, the nut has been augmented with a radially-extending rib
1468 on the periphery thereof as can be best seen in FIGS. 123 and
125. A distal end of the second arm 1440 has been modified with an
inwardly-extending rib 1470 as also can be seen in FIGS. 123 and
125.
A connector arm 1472 interconnects the nut 1466 with the second arm
1440. The connector arm has first and second ends 1474, 1476
provided with oppositely- and laterally-extending sockets 1478,
1480, respectively. The socket 1478 on the first end 1474 of the
connector arm 1472 receives the rib 1468 on the nut 1466. The
socket 1480 on the second end 1476 of the connector arm 1472
receives the rib 1470 on the second arm 1440. Each socket and rib
combination forms a hinge pivotable about an axis normal to the
drawing orientation of FIGS. 123 125 to contain movement of the nut
along the worm 1464. In this manner, the second arm 1440 is
interconnected with the nut 1466 and is moved with respect to the
first arm 1438 when the motor 1460 is actuated, thus rotating both
the output shaft 1462 and the worm 1464, causing the nut 1466 to
travel along the worm 1464 with the rotation thereof.
In use, when the mirror assembly 1430 is in the retracted position
as shown in FIGS. 122 123, the driver 1318 actuates the motor 1460
through a switch (not shown) to signal the extension of the mirror
assembly 1430 to begin moving to the extended position. Whatever
the method by which the motor 1460 is actuated, the motor 1460
imparts rotation to the output shaft 1462 and, in turn, to the worm
1464 causing the nut 1466 to travel therealong. When the mirror
assembly is being moved from the retracted to the extended
position, the nut 1466 moves from an inner end of the worm 1464
adjacent to the output shaft 1462 toward the end distal therefrom.
Conversely, the nut 1466 moves from the distal end of the worm 1464
toward the inner adjacent to the output shaft when the mirror
assembly 1430 moves from the extended position to the retracted
position.
It will be understood that the mirror assembly 1430 can also be
signaled to move between the retracted and extended positions by a
generally conventional microcontroller (not shown) which can be
configured in a well-known manner to move the mirror assembly 1430
between the extended and retracted positions based upon a
predetermined event. Examples of such triggering events can
include, but are not limited to, ignition or shut-off of the
vehicle motor, position of the vehicle transmission into a
particular gear (e.g., reverse), closure of a vehicle door, and the
like.
While the embodiments shown in FIGS. 114 125 accomplish the
repositioning of the mirror 1334, 1434 by extension and retraction
of the mirror housing along an arcuate path, it will be understood
that this is but one method by which the automatic repositioning of
the mirror 1334, 1434 relative to the housing 1342, 1442 can be
accomplished. An additional embodiment of the invention
incorporating this feature is shown in FIGS. 126 127 in which a
mirror assembly with a linear extension is shown, and in which the
adjuster for the mirror is a cam device which pivots the mirror
relative to the mirror housing and the base to compensate for the
movement of the mirror housing. It will be understood that
reference numerals in FIGS. 126 127 have been increased by 200 for
components common to the embodiments shown in FIGS. 114 121 and
have been increased by 100 for components common to the embodiment
shown in FIGS. 122 125. These common components and/or elements
need not be re-described but their description can be incorporated
by reference from the previous embodiments.
FIG. 126 shows this new embodiment in a retracted position and FIG.
127 shows this new embodiment in an extended position. It can be
seen from an examination of these figures that the first and second
arms 1538, 1540 of the adjuster 1536 are linear arms as contrasted
with the arcuately-configured arms of the previous embodiments.
An outer surface of the first arm 1538 between a first end 1582 and
a second end 1584 thereof.
The second arm 1540 has a rounded rectangular slot 1586 on an outer
surface thereof in coaxial alignment with the slot 1580 on the
first arm 1538 and extending circumferentially a sufficient extent
to overlap the slot 1580 regardless of the particular longitudinal,
angular or rotational position of the first arm 1538 with respect
to the second arm 1540. A distal end of the second arm 1540 also
has an outwardly-extending gimbal 1588 thereon.
The mounting plate 1550 is augmented with a backplate having a
socket 1590 adjacent to a first end 1592 thereof, the opposite end
1594 of the backplate has an outwardly-extending flange 1596
thereon. The flange 1596 has a normally-extending pin 1598
thereon.
In assembly, the first and second arms 1538 and 1540 are
telescopingly received by each other so that the slot 1580 in the
first arm 1538 overlaps the slot 1586 in the second arm 1540. The
mounting plate 1550 is attached to the second arm 1540 so that the
gimbal 1588 on the distal end of the second arm 1540 is received by
the socket 1590 on the backplate of the mounting plate 1550,
thereby pivotally mounting the mounting plate 1550 (and therefore
the mirror 1534) to the second arm 1540. The pin 1598 is thereby
received in the aperture created by the overlap of the slots 1580
and 1586 in the first and second arms 1538 and 1540, thus pinning
the pivotal position of the mounting plate 1550 to the position of
the second arm 1540 with respect to the first arm 1538. When the
mounting plate 1550 is so mounted, the angular position of the
mounting plate 1550 and mirror 1534 subassembly is dependent upon
the position of the second arm 1540 with respect to the first arm
1538.
The configuration and positioning of the slots 1580 and 1586 on the
first and second arms 1538 and 1540 are preferably selected so that
the field of view encountered by the driver 18 is virtually the
same regardless of the amount of extension of the mirror housing
1542 with respect to the base 1532. In this manner, the driver 18
does not need to readjust the mirror when using the mirror
extension function.
In use, when the mirror 1534 and housing 1542 are in the retracted
positions, the pin 1598 on the mounting plate 1550 extends through
the aligned slots 1580, 1586 in the first and second arms 1538,
1540, respectively, adjacent to the first end 1582 of the slot
1580. Then, after an appropriate actuation is received (i.e.,
actuation of a power extend motor or a user simply grasping the
mirror housing 1542 and pulling it outwardly with respect to the
base 1532), the mirror housing 1542 begins to move toward the
extended position. In this manner, the pin 1598 moves within the
slot 1580 toward the second end 1584 thereof. Because the movement
of the pin 1598 is constrained within the aligned slots 1580 and
1586, the mounting plate 1550 (and, thus, the mirror 1534) pivots
about the gimbal 1588 and socket 1590 mounting between the second
arm 1540 and the mounting plate 1550, respectively.
It can be seen from the drawings that the mounting plate 1550 and
the mirror 1534 will pivot counterclockwise (in the orientation
shown in FIGS. 126 127) when the adjuster 1536 moves from the
retracted position (see FIG. 126) to the extended position (see
FIG. 127). It can also be seen that the converse is true in that
the mounting plate 1550 and the mirror 1534 pivot clockwise (in the
orientation shown in FIGS. 126 127) when the adjuster 1536 moves
from the extended position (see FIG. 127) to the retracted position
(see FIG. 126).
It will be understood that the embodiment shown in FIGS. 126 127,
although shown in a manual form, can also be combined with a motor
for a power-extend feature as shown in the previous
embodiments.
It will also be understood that a combination of the cam device
shown in FIGS. 126 127 with a set of linear extension arms can be
combined with a mirror assembly having arcuate extension arms (see
components labeled with reference numerals 1238, 1240, 1438, 1440)
for additional facilitation and control of the movement of the
mirror assembly between the retracted and extended positions while
providing desirable compensation for the mirror view plane angle as
previously described.
A tenth embodiment of the invention is applicable in any situation
where it is desirable to drive at least two independent outputs
from a single motor. One such application is illustrated in FIG.
128 in a vehicle rear view mirror 1700. This application shows the
use of a single motor according to the invention in two
environments: (1) as a driver for a power fold function of the
rearview mirror 1700, and (2) as a driver for a power extend
function of the rearview mirror 1700. The power fold and extend
embodiment is illustrated in FIGS. 128 141. In this embodiment, one
output shaft of the motor drives the power fold function and the
other output shaft drives the power extend function.
Looking at FIGS. 128 141, the rearview mirror 1700 comprises a
support 1704 adapted to mount to the vehicle 12, and which is made
of a cover 1706 and a mirror receptacle 1708, nested within the
cover 1706. A pivot mechanism 1710 is fixedly secured in a socket
1712 in the mirror receptacle 1708. A carriage arm 1714 pivots on
the pivot mechanism 1710 and carries a motor assembly 1716
according to the invention. A power fold drive shaft 1718 and a
power extend drive shaft 1720 extend from the motor assembly 1716.
The power fold drive shaft 1718 engages the pivot mechanism 1710 in
a manner hereinafter described to cause the carriage arm 1714 to
pivot relative to the support 1704. The power extend drive shaft
1720 is a worm screw that carries a threaded nut 1722 secured to a
shaft 1724. A carriage bracket 1726 and a shell bracket 1728 are
mounted to each other and to the shaft 1724. The carriage bracket
1726 carries a conventional mirror assembly 1730 which may or may
not include a tilt mechanism 1732. The shell bracket 1728 provides
support for a mirror housing 1734.
Looking more closely at FIG. 128, the pivot mechanism 1710
comprises an outer housing 1736 and a cover 1738 which enclose a
ramp 1740, a wave spring 1742, and an actuator sub 1744. Referring
also to FIGS. 129 and 130, the outer housing 1736 is a generally
cylindrically-shaped body comprising a cylindrical wall 1746 and a
collar 1748 connected to the cylindrical wall 1746 by an annular
wall 1750 and coaxial therewith. The annular wall 1750 extends
orthogonally inwardly from the cylindrical wall 1746 to the collar
1748. Referring to FIG. 130, the inner surface of the annular wall
1750 is provided with a pair of diametrically-opposed inner bosses
1752 extending downwardly from the annular wall 1750. The collar
1748 comprises a generally ring-shaped structure defining a
circular opening 1754. The cylindrical wall 1746 defines a
cylindrical chamber 1756. Extending orthogonally outwardly from the
cylindrical wall 1746 at an opposite end from the collar 1748 is a
base ring 1758 circumscribing the cylindrical wall 1746. The base
ring 1758 is provided with a plurality of mounting bosses 1760
spaced above the periphery of the cylindrical wall 1746 and having
a mounting bore 1762 extending therethrough generally parallel to
the longitudinal axis of the outer housing 1736. Extending
downwardly from the base ring 1758 are a pair of
diametrically-opposed mounting pegs 1764 generally parallel to the
longitudinal axis of the outer housing 1746.
Referring now to FIGS. 131 135, the ramp 1740 is a ring-like body
comprising a pair of diametrically-opposed thin ring segments 1766
in alternating juxtaposition with a pair of diametrically-opposed
raised segments 1768. The raised segments 1768 transition to the
thin ring segments 1766 through terminal ends defined by a first
inclined face 1770 and a second inclined face 1772. The thin ring
segments 1766 and the raised segments 1768 define a circular inner
wall 1774 defining a generally circular center opening 1776.
Regularly spaced along the inner wall 1774 are a plurality of
notches 1778. In the embodiment shown in FIG. 131, six notches 1778
are shown in diametrically-opposed pairs. One pair of notches 1778
bisect the raised segments 1768, and the remaining notches 1778 are
formed at each end of the thin ring segments 1766.
The wave spring 1742 is a generally helical spring formed of a flat
ribbon of metal, preferably spring steel having alternating crest
portions 1780 and trough portions 1782. The spring 1742 is formed
so that the trough portions 1782 of one coil contact the crest
portions 1780 of the adjoining coil. Preferably, the portions in
contact with one another are fixedly connected, such as by spot
welding. The spring 1742 defines a circular center opening
1784.
The actuator sub 1744 is a generally cylindrically-shaped body
comprising a generally cylindrical lower housing 1786 and a
generally cylindrical upper housing 1788. The lower housing 1786
comprises a lower cylindrical wall 1790 transitioning to an
inwardly-extending annular wall 1792 which, in turn, transitions to
an upper cylindrical wall 1794 of the upper housing 1788. The lower
cylindrical wall 1790 is provided with a plurality of peripheral
slots 1796 spaced thereabout at an opposite end from the upper
housing 1788. The upper cylindrical wall 1794 transitions to an
annular top wall 1798 having a depending inner peripheral wall 1810
defining a circular opening 1812. The upper cylindrical wall 1794
is provided with a plurality of regularly-spaced ribs 1814
extending longitudinally along the upper cylindrical wall 1794 from
the annular wall 1792. The ribs 1814 are adapted to slidably engage
the notches 1778 in the ramp 1740 when the upper housing 1788 is
inserted through the center opening 1776. A plurality of seats 1816
are spaced regularly around the upper housing 1788 at the inner
face of the top wall 1798 and the upper cylindrical wall 1794.
Preferably, the seats 1816 are spaced at 120 degrees around the
periphery of the upper cylindrical wall 1794. Upper housing sockets
1818 comprise circular apertures through the top wall 1798 at
regularly-spaced intervals. Preferably, the sockets 1818 are spaced
at 120 degrees around the top wall 1798.
As shown in FIGS. 136 and 137, the wave spring 1742 is placed over
the upper housing 1788 so that the upper housing 1788 extends
through the center opening 1784. The ramp 1740 is then placed over
the upper housing 1788 to abut the wave spring 1742 so that the
upper housing 1788 extends through the center opening 1776. The
wave spring 1740 will urge the ramp 1740 in a direction away from
the annular wall 1792.
Referring to FIG. 134, a plurality of actuator sub ring channels
1820 comprise longitudinal channels in the inner portion of the
lower cylindrical wall 1790 generally parallel to the longitudinal
axis of the actuator sub 1744. The channels 1820 extend along the
lower cylindrical wall 1790 from the open end of the actuator sub
1744. In this embodiment, three channels 1820 are spaced at 120
degrees along the interior of the lower cylindrical wall 1790. A
circumferential C-ring channel 1822 extends around the periphery of
the lower cylindrical wall 1790 along the inner surface thereof
adjacent the opening to the actuator sub 1744.
Referring again to FIGS. 135 136, an actuator sub ring 1830 is a
generally ring-like body comprising an annular wall 1832 defining a
circular opening 1834. A plurality of slots 1836 are cut into the
ring 1830 at regularly spaced intervals, preferably 90 degrees, to
define segments 1838. A plurality of outwardly-extending ribs 1840
is spaced about the outer periphery of the ring 1830, preferably at
120 degrees. The actuator sub ring 1830 is adapted to be slidably
inserted into the actuator sub 1744 and the ribs 1840 are adapted
to be slidably inserted into the actuator sub ring channels 1820 as
shown in FIG. 136.
A ring gear 1842 comprises an annular body 1844 defining a circular
opening 1846. An upper surface of the annular body 1844 includes a
plurality of bosses 1848, preferably at regularly-spaced radial
locations thereon. In the preferred embodiment, four bosses 1848
are spaced at intervals of 90 degrees. The inner surface of the
annular body 1844 is provided with a plurality of teeth 1850 in
longitudinal alignment with the axis of the ring gear 1842. The
bosses 1848 are adapted to slidably engage the slots 1836 in the
actuator sub ring 1830. The ring gear 1842 is adapted to be
slidably inserted into the actuator sub 1744, as shown in FIG.
136.
As also shown in FIG. 136, a spring 1852 comprises a generally
conventional helical spring adapted to be slidably inserted into
the actuator sub 1744 and abut the annular wall 1832 and the
actuator sub ring 1830. A conventional C-ring 1854 is adapted to be
retained within the C-ring channel 1822 in a generally conventional
manner. As shown in FIG. 136, the spring 1852 is slidably inserted
into the actuator sub 1744 to abut the annular wall 1792. The
actuator sub ring 1830 is then inserted into the actuator sub 1744
so that the ribs 1840 slidably communicate with the actuator sub
ring channels 1820, to abut the slots 1836 extending away from the
spring 1852. The ring gear 1842 is then slidably inserted into the
actuator sub 1744 so that the bosses 1848 engage the slots 1836.
The spring 1852, the actuator sub ring 1830, and the ring gear 1842
are retained in the actuator sub 1744 by compressively inserting
the C-ring 1854 into the C-ring channel 1822.
The pivot mechanism 1710 is assembled as shown in FIGS. 128 and
131. The wave spring 1742 is inserted over the upper housing 1788
of the actuator sub 1744. The ramp 1740 is then inserted over the
upper housing 1788 of the actuator sub 1744 to abut the wave spring
1742 so that the raised segments 1768 extend axially away from the
lower housing 1786. The spring the 1852, the actuator sub ring
1830, and the ring gear 1842 are assembled into the lower housing
1786 of the actuator sub 1744 as previously described and retained
therein with the C-ring 1854. The assembled actuator sub 1744 is
then inserted into the outer housing 1736 so that the upper housing
1788 extends through the opening 1754 and the actuator sub 1744 is
in slidable communication with the outer housing 1736 for
rotational movement relative thereto. The cover 1738 is secured to
the outer housing 1736 to retain the actuator sub 1744 therein. The
cover 1738 has a hole 1872 to receive the power fold drive shaft
1718. The seats 1816 and sockets 1818 in the top wall 1798 of the
actuator sub 1744 are used to locate and secure the actuator sub
1744 in the socket 1712.
Referring now to FIGS. 128, and 138 140, the carriage arm 1714 has
a turret 1874 sized to fit over the cover 1738 and outer housing
1736 of the pivot mechanism 1710 and rotate relative thereto. The
carriage arm 1714 includes a seat 1876 sized and shaped to receive
and retain the motor assembly 1716. An aperture 1878 in a bottom
wall 1879 of the seat 1876 is open to the turret 1874 and
positioned to be in registry with the hole 1872 in the cover 1738
of the pivot mechanism 1710. When the motor assembly 1716 is seated
in the seat 1876, the power fold drive shaft 1718 extends
downwardly through the aperture 1878 and the hole 1872 into the
pivot mechanism 1710. A gear 1880 on the power fold drive shaft
1718 engages the teeth 1850 of the ring gear 1842.
The carriage arm 1714 also includes an elongated channel 1882 which
receives the power extend drive shaft 1720, which in turn carries
the threaded nut 1722 and the shaft 1724. A pair of upstanding pins
1884 extend upwardly from the channel 1882 adjacent to one side and
some guide surfaces 1886 are provided on the outside of the channel
1882. The distal end of the channel 1882 has a seat 1888 with a
semi-circular bearing surface 1890 therein. The shaft 1724 is sized
to reciprocate on the bearing surface 1890 of the seat 1888, which
provides support for the shaft 1724 as it moves with the nut 1722
by the power extend drive shaft 1720.
Looking also at FIG. 141, the shell bracket 1728 is secured by
conventional means to the carriage bracket 1726 with the carriage
arm 1714 between them. The shaft 1724 has pair of wings 1892 at its
distal end. The shell bracket 1728 has a bearing surface 1902
adapted to ride on one of the guide surfaces 1886 of the carriage
arm 1714. It also has a mounting tab 1904 positioned to connect to
one of the wings 1892 of the shaft 1724. The carriage bracket 1726
also has a guide surface 1906 adapted to ride on another of the
guide surfaces 1886 of the carriage arm 1714, and it also has a
mounting tab 1908 positioned to connect to the other of the wings
1892 of the shaft 1724. It will be apparent that with this
structure, as the shaft 1724 moves, so does the shell bracket 1728
and the carriage bracket 1726.
Looking now more closely at FIGS. 139 and 140, the motor assembly
1716 will be described, as it is adapted to the present application
in the rearview mirror 1700. Like numerals will be used to identify
like elements except as otherwise indicated. The motor assembly
1716 comprises a case 1913 having a compartment 1614 in which a
motor 1615, a drive shaft 1616, and a spring 1634 are disposed. The
spring 1634 biases the motor 1615 so that a first clutch 1650
engages a first output shaft 1652 in driving engagement with the
drive shaft 1616 at a low motor speed. Simultaneously, a second
clutch 1654 disengages a second output shaft 1656 from the drive
shaft 1616. At a higher motor speed, a fly 1636 causes the motor
1615 to move against the bias of the spring 1634 so that the clutch
1654 engages the second output shaft 1656 with the drive shaft 1616
and disengages the first output shaft 1652 from the drive shaft
1616.
A first transfer gear 1914 is disposed adjacent to a worm gear 1664
on the first output shaft 1652 to transfer power to a first drive
gear 1916. The transfer gear 1914 will have a toothed portion to
engage the worm gear 1664 and a worm portion to engage the first
drive gear 1916. Similarly, a second transfer gear 1918 is disposed
adjacent to a worm gear 1674 on the second output shaft 1656 to
transfer power to a second drive gear 1920. Like the first transfer
gear 1914, the second transfer gear 1918 will have a toothed
portion to engage the worm gear 1674 and a worm portion to engage
the second drive gear 1920. The second drive gear 1920 further has
an extension shaft 1922 that terminates in a first pinion gear 1924
which engages a second pinion gear 1926 at the upper end of the
power fold drive shaft 1718. The first drive gear 1916 is connected
axially to the power extend drive shaft 1720.
Operation of the power extend function is accomplished by
energizing the motor 1615 at a low voltage B, thus driving the
first output shaft 1652 and the power extend shaft 1720 via the
first transfer gear 1914 and the first drive gear 1916. Rotation of
the power extend shaft 1720 causes a threaded nut 1722 to traverse
the shaft 1720, depending upon the direction of rotation. As the
nut 1722 moves, so does the shaft 1724 and also the rest of the
mirror structure connected thereto by way of the shell bracket 1728
and the carriage bracket 1726. When the motor 1615 is operated in
one direction, the mirror assembly 1730 is thus urged away from the
mirror support 1704, and when the motor 1615 is operated in the
opposite direction, the mirror assembly 1730 is urged toward the
mirror support 1704.
When the motor 1615 is energized at a high voltage A, centrifugal
force on the fly 1636 due to higher speed of the motor 1615 causes
disengagement of the first output shaft 1652 and engagement of the
second output shaft 1656, driving the power fold drive shaft 1718
via the second transfer gear 1918, the second drive gear 1920, the
extension shaft 1922 and the pinion gears 1924, 1926. Rotation of
the gear 1880 on the power fold drive shaft 1718 acting against the
teeth 1850 of the ring gear 1842 in the pivot mechanism 1710 walks
the gear 1880 around the ring gear 1842, causing the entire
carriage arm 1714 to rotate relative to the pivot mechanism
1710.
If the mirror assembly 1730 is forcibly pivoted, such as would
occur if it were to strike an immovable object, the actuator sub
ring 1830 is separated from engagement with the ring gear 1842. The
actuator sub ring 1830 can ride against the underside of the ring
gear 1842 against the bias of the spring 1852 until the detents
1848 re-engage with the slots 1836 on the actuator sub ring 1830
whereupon the motor 1615 can once again drive the rotation of the
carriage arm 1714.
While the invention has been specifically described in connection
with certain specific embodiments thereof, it is to be understood
that this is by way of illustration and not of limitation.
Reasonable variation and modification are possible within the scope
of the foregoing disclosure and drawings without departing from the
scope of the invention.
* * * * *